KR102508198B1 - Rotary compressor - Google Patents

Abstract

A rotary compressor according to the present embodiment may comprise an outflow passage through which refrigerant flows out of a compression space. The outflow passage may include: a first outflow guide portion disposed in a main bearing or a sub bearing; a second outflow guide portion formed through between both axial ends of a roller; and a third outflow guide portion disposed in a bearing opposite to the bearing including the first outflow guide portion with respect to the roller and communicating with the first outflow guide portion through the second outflow guide portion. Accordingly, the amount of refrigerant remaining in the compression space can be minimized to improve compression efficiency. In addition, a pressure difference at the front of a vane can be eliminated to suppress vane jumping, thereby reducing the abrasion of the vane or a cylinder. Moreover, the outflow passage can be periodically opened to suppress the leakage of the refrigerant during a compression stroke, thereby preventing insufficient compression.

Description

Rotary compressor {ROTARY COMPRESSOR}

The present invention relates to a vane-type rotary compressor in which vanes are slidably inserted into rotating rollers.

The rotary compressor can be divided into a method in which a vane is slidably inserted into a cylinder and contacted with a roller, and a method in which a vane is slidably inserted into a roller and contacted with a cylinder. The former is referred to as an eccentric rotary compressor, and the latter is classified as a vane rotary compressor (or concentric rotary compressor).

In the eccentric rotary compressor, a vane inserted into a cylinder is pulled toward a roller by an elastic force or a back pressure force and comes into contact with the outer circumferential surface of the roller. On the other hand, in the vane rotary compressor, the vane inserted into the roller rotates together with the roller, and is drawn toward the cylinder by centrifugal force and back pressure, and comes into contact with the inner circumferential surface of the cylinder.

The eccentric rotary compressor independently forms compression chambers as many as the number of vanes per rotation of the roller, and each compression chamber simultaneously performs suction, compression, and discharge strokes. On the other hand, the vane rotary compressor continuously forms compression chambers as many as the number of vanes per rotation of the roller, and each compression chamber sequentially performs suction, compression, and discharge strokes. Therefore, the vane rotary compressor forms a higher compression ratio than the eccentric rotary compressor. Accordingly, the vane rotary compressor is more suitable for using high-pressure refrigerants having low ozone depletion potential (ODP) and global warming potential (GWP), such as R32, R410a, and CO ₂ .

Patent Document 1 (US Patent Publication No. US2014/0369878 A1), Patent Document 2 (Japanese Patent Application Publication No. 2000-265984) and Patent Document 3 (Japanese Patent Application Publication No. 2013-72429) each disclose a vane rotary compressor. These vane rotary compressors are provided with a contact point between the discharge port and the suction port where the outer circumferential surface of the roller and the inner circumferential surface of the cylinder are almost in contact, so that the discharge port and the suction port are separated.

However, in the conventional vane rotary compressor, a gap is generated between the discharge port and the contact point in the circumferential direction, so that the entire amount of the compressed refrigerant is not discharged in the discharge stroke, and some of the compressed refrigerant remains in the space between the discharge port and the contact point. It can be. This refrigerant flows back into the compression chamber that follows, resulting in overcompression, which increases the motor input and reduces the efficiency of the compressor.

In addition, in the conventional vane rotary compressor, the pressure on the front side of the vane rises excessively due to the overcompression of the residual refrigerant, causing the vane to vibrate. The front surface of the cylinder or the inner circumferential surface of the cylinder may be damaged, which may reduce the reliability of the compressor.

In addition, in the conventional vane rotary compressor, the refrigerant during the compression stroke flows back to the suction stroke side while the vibrating phenomenon of the vane continues, thereby heating the refrigerant on the suction stroke side. As a result, the specific volume of the suctioned refrigerant increases and the intake amount of the refrigerant decreases, resulting in suction loss, which may reduce the efficiency of the compressor.

In addition, in the conventional vane rotary compressor, when a discharge port is formed in the cylinder, the surface pressure between the front surface of the vane passing through the discharge port and the inner circumferential surface of the cylinder increases but is not formed uniformly, so that the front surface of the vane or the inner circumferential surface of the cylinder may wear out. In addition, as the valve-receiving groove is formed on the outer circumferential surface of the cylinder, the processing of the cylinder becomes complicated, resulting in an increase in manufacturing cost. can be aggravated.

US Patent Publication US2014/0369878 A1 (published date: 2014.12.18.) Japanese Laid-open Patent No. 2000-265984 (Publication date: 2000.09.26.) Japanese Laid-open Patent No. 2013-72429 (Publication date: 2013.04.22.)

An object of the present invention is to provide a rotary compressor capable of reducing the residual amount of refrigerant remaining in the compression space without being discharged.

Furthermore, an object of the present invention is to provide a rotary compressor capable of suppressing the outflow of refrigerant during a compression stroke while reducing the residual amount of refrigerant in a compression space.

Furthermore, an object of the present invention is to provide a rotary compressor in which the remaining space can be periodically communicated with the inner space of the casing.

Another object of the present invention is to provide a rotary compressor capable of rapidly discharging refrigerant during a discharge stroke.

Furthermore, an object of the present invention is to provide a rotary compressor capable of increasing a refrigerant discharge amount by increasing a refrigerant discharge effective area.

Furthermore, an object of the present invention is to provide a rotary compressor capable of extending a substantial discharge stroke.

Another object of the present invention is to provide a rotary compressor capable of reducing the vibration noise of the compressor while suppressing vane or cylinder wear.

Furthermore, an object of the present invention is to provide a rotary compressor capable of eliminating the difference between the pressure acting on the front surface of the vane and the back pressure acting on the rear surface of the vane.

Furthermore, an object of the present invention is to provide a rotary compressor capable of equalizing the pressure acting on the front surface of the vane.

Another object of the present invention is to provide a rotary compressor capable of suppressing vibration of a vane even when a high-pressure refrigerant such as R32, R410a, or CO ₂ is used.

A rotary compressor for achieving the object of the present invention may include a casing, a cylinder, a roller, a vane, a main bearing, a sub-bearing, and a discharge passage. The casing has a sealed inner space. The cylinder is provided in the inner space of the casing to form a compression space. The roller is provided on a rotating shaft so as to be rotatable inside the cylinder, and is positioned eccentrically with respect to the center of the compression space so as to have a contact point close to the inner circumferential surface of the cylinder. The vane is slidably inserted into a vane slot provided on the roller and rotates together with the roller. The main bearing and the sub-bearing are disposed on both sides of the cylinder in the axial direction, respectively, and form a compression space together with the cylinder. A portion of the discharge passage may be formed through the roller. Accordingly, the remaining space after the discharge stroke or the compressed space during the discharge stroke may be periodically communicated with the inner space of the casing according to the rotation angle of the roller. Through this, the structure of the cylinder can be simplified and easily processed, and the surface pressure between the vane and the cylinder around the discharge hole can be lowered and the vibrating phenomenon of the vane can be reduced to suppress wear and vibration noise between the vane and the cylinder. In addition, the residual amount of refrigerant in the compression space can be reduced by discharging the refrigerant remaining in the residual space or by quickly discharging the refrigerant during the discharge process. In addition, by reducing the pressure difference between the front and rear of the vane, wear and vibration noise caused by vibration of the vane can be reduced.

For example, the discharge passage may be periodically opened according to rotation of the roller. Through this, while the refrigerant is periodically discharged after the discharge stroke or during the discharge stroke, under-compression can be prevented by suppressing the discharge of the refrigerant before the discharge stroke in advance.

In addition, the discharge passage may be provided with a plurality at equal intervals along the circumferential direction of the roller. Through this, the discharge passage is opened at the same rotation angle, so that the refrigerant after the discharge stroke or during the discharge stroke can be periodically discharged at regular intervals.

In addition, a plurality of vane slots may be formed along the circumferential direction of the roller. A portion of the discharge passage may be formed between the plurality of vane slots. Through this, the refrigerant compressed in each compression chamber can be periodically discharged through each back pressure passage according to the rotation angle of the roller.

In addition, a rotary compressor for achieving the object of the present invention may include a casing, a cylinder, a roller, a vane, a main bearing, a sub-bearing, and a discharge passage. The casing has a sealed inner space. The cylinder is provided in the inner space of the casing to form a compression space. The roller is provided on a rotating shaft so as to be rotatable inside the cylinder, and is positioned eccentrically with respect to the center of the compression space so as to have a contact point close to the inner circumferential surface of the cylinder. The vane is slidably inserted into a vane slot provided on the roller and rotates together with the roller. The main bearing and the sub-bearing are disposed on both sides of the cylinder in the axial direction, respectively, and form a compression space together with the cylinder. The discharge passage includes a first discharge guide, a second discharge guide and a third discharge guide to discharge the refrigerant from the compression space to the inner space of the casing. The first discharge guide part is provided on the main bearing or the sub-bearing. The second discharge guide may pass between both ends of the roller in an axial direction and communicate with the first discharge guide. The third discharge guide part is provided on a bearing opposite to the bearing provided with the first discharge guide part around the roller, and may communicate with the first discharge guide part through the second discharge guide part. Through this, the remaining refrigerant in the compression space is reduced by discharging the refrigerant remaining in the residual space, and at the same time, the effective discharge area is enlarged so that the compressed refrigerant is quickly discharged, thereby reducing the residual amount of the refrigerant and improving the compression efficiency. In addition, vane jumping can be suppressed by eliminating the pressure difference on the front surface of the vane, thereby reducing vane or cylinder wear. In addition, as the discharge passage is periodically opened, leakage of the refrigerant during the compression stroke can be suppressed, thereby preventing under-compression from occurring.

For example, the second discharge guide unit may be in periodic communication with the first discharge guide unit. Through this, it is possible to suppress leakage of the compressed refrigerant while reducing the residual amount of the refrigerant.

As another example, the second discharge guide unit may be in periodic communication with the third discharge guide unit. Through this, it is possible to suppress leakage of the compressed refrigerant while reducing the residual amount of the refrigerant.

As another example, the first discharge guide unit may be in periodic communication with the third discharge guide unit by the second discharge guide unit when the roller rotates. Through this, it is possible to suppress leakage of the compressed refrigerant while reducing the residual amount of the refrigerant.

As another example, the number of the second discharge guides may be greater than the number of the first discharge guides or the number of the third discharge guides. Through this, it is possible to suppress leakage of the refrigerant under compression while smoothly discharging the refrigerant in the remaining space.

Specifically, the first discharge guide unit and the third discharge guide unit may be provided one by one. The second discharge guide portion may be provided with a plurality and formed at predetermined intervals along the circumferential direction. Through this, the discharge passage for discharging the residual refrigerant may be opened once per rotation of the roller and periodically opened in the residual space communicating with the final compression chamber.

In addition, the first discharge guide and the third discharge guide facing the second discharge guide may be formed on the same axis. The second discharge guide portion may be penetrated in an axial direction. Through this, the length of the second discharge guide can be minimized to facilitate processing of the second discharge guide and at the same time, residual refrigerant can be quickly discharged.

In addition, the first discharge guide and the third discharge guide facing the second discharge guide may be formed on different axes. The second discharge guide portion may be penetrated obliquely with respect to the axial direction. Through this, it is possible to facilitate the processing of the first discharge guide and at the same time increase the degree of freedom in the design of the first discharge guide. In addition, as the second discharge guide portion is inclined, the centrifugal force for the refrigerant passing through the second discharge guide portion increases, so that the remaining space or the compressed space during the discharge stroke can be discharged more quickly.

As another example, the first discharge guide unit may include a first guide groove communicating with the compression space; and a second guide groove having one end communicating with the first guide groove and the other end communicating with the second discharge guide unit. The second guide groove may extend closer to the center of rotation of the roller than the first guide groove. Through this, the refrigerant in the remaining space can be discharged into the inner space of the casing by periodically passing through the rollers.

Specifically, at least one discharge port may be formed in the main bearing or the sub-bearing. At least a portion of the first guide groove may overlap the discharge port in an axial direction. Through this, the effective discharge area of the refrigerant can be expanded so that the refrigerant can be quickly discharged from the compression space or the residual refrigerant can be smoothly discharged.

More specifically, the first guide groove may overlap the discharge port by at least 50% or more in the axial direction. Through this, the effective discharge area of the refrigerant is further enlarged so that the refrigerant can be more quickly discharged from the compression space or the remaining refrigerant can be more smoothly discharged.

In addition, at least one discharge port may be formed in the main bearing or the sub-bearing. The first guide groove may be formed to have a cross-sectional area larger than or equal to a cross-sectional area of the discharge port where the first guide groove overlaps in an axial direction. Through this, the refrigerant can be more quickly discharged from the compression space or the remaining refrigerant can be more smoothly discharged.

In addition, at least one discharge port may be formed in the main bearing or the sub-bearing. The first guide groove may be formed to be positioned at a rear side relative to the rotational direction of the roller relative to the discharge port overlapping the first guide groove in the axial direction. Through this, it is possible to effectively discharge residual refrigerant remaining in the residual space after the discharge stroke to increase compression efficiency and at the same time suppress vane jumping to suppress vane or cylinder wear.

For example, a plurality of first guide grooves may be provided along the circumferential direction, and an intermediate connection groove for communicating the plurality of first guide grooves with each other may be provided between the plurality of first guide grooves. Through this, the discharge passage extends to the circumferential range of the compression chamber or outside the circumferential range of the compression chamber, thereby minimizing the residual amount of refrigerant. In addition, as the arc length of the discharge passage is formed equal to or longer than the arc length of the compression chamber, continuous discharge is possible and pressure pulsation can be reduced.

In addition, at least one discharge port may be formed in the main bearing or the sub-bearing. The first guide groove may be formed to be positioned at a front side relative to the rotational direction of the roller relative to the discharge port overlapping the first guide groove in the axial direction. Through this, the effective discharge area of the refrigerant can be expanded so that the refrigerant in the compression chamber can be discharged more quickly, and the amount of refrigerant moving to the residual space can be reduced and the residual amount of refrigerant can be suppressed.

For example, a plurality of discharge ports may be formed in the main bearing or the sub-bearing. The first guide groove may be positioned between the plurality of discharge ports to communicate with each of the plurality of discharge ports. Through this, the effective discharge area of the discharge port is enlarged so that the refrigerant in the compression chamber can be rapidly discharged.

In addition, a plurality of back pressure pockets having different pressures may be formed spaced apart from each other in a circumferential direction on one side surface of the main bearing and one side surface of the sub bearing facing the roller in the axial direction. The second guide groove may be formed to be thinner and longer than the first guide groove and may be provided between the plurality of back pressure pockets in a circumferential direction. Through this, the discharge passage can be formed to be periodically opened through the roller.

As another example, a plurality of vane slots may be formed along the circumferential direction. The second discharge guide part may be provided between each of the vane slots adjacent to each other in the circumferential direction. Through this, the discharge passage is periodically opened to reduce the residual amount of the refrigerant while suppressing leakage of the compressed refrigerant.

In addition, at least one end of both ends of the second discharge guide and an end of the first discharge guide facing the second discharge guide and an end of the third discharge guide may be formed with an expansion groove having an enlarged cross-sectional area. Through this, the residual refrigerant can be discharged more quickly by increasing the period in which the discharge passages communicate with each other and are opened.

As another example, a plurality of back pressure pockets having different pressures may be spaced apart from each other in a circumferential direction on one side surface of the main bearing and one side surface of the sub bearing facing the roller in the axial direction. The third discharge guide part may be provided between the plurality of back pressure pockets in a circumferential direction. Through this, the discharge passage is periodically opened to reduce the residual amount of the refrigerant while suppressing leakage of the compressed refrigerant.

As another example, a discharge muffler accommodating a discharge port may be provided in the main bearing or the sub-bearing. The third discharge guide part may open toward an inner space of the casing from the outside of the discharge muffler. Through this, as the refrigerant is discharged from the outside of the discharge muffler, the increase in the internal pressure of the discharge muffler is suppressed, so that the discharge valve is quickly opened, and at the same time, the vortex phenomenon in the discharge space is suppressed, so that the refrigerant is discharged more quickly from each outlet. can be ejected.

Specifically, the main bearing or the sub-bearing may include a plate portion coupled to an axial side surface of the cylinder; and a boss portion extending in an axial direction from one side of the plate portion in an axial direction and through which the rotating shaft passes. The third discharge guide part may open toward the inside of the casing from the boss part.

As another example, a discharge muffler accommodating a discharge port may be provided in the main bearing or the sub-bearing. The third discharge guide portion may be opened toward an inner space of the discharge muffler. Through this, it is possible to easily process the discharge passage by reducing the length of the discharge passage provided in the bearing.

Specifically, the main bearing or the sub-bearing may include a plate portion coupled to an axial side surface of the cylinder; and a boss portion extending in an axial direction from the plate portion and through which the rotating shaft passes. The third discharge guide part may pass through the plate part.

As another example, a discharge port opened and closed by a discharge valve may be provided in one of the main bearing and the sub-bearing. The first discharge guide part may be formed in a bearing not provided with the discharge port. Through this, the refrigerant remaining in the compression space is periodically discharged to reduce the amount of residual refrigerant and prevent under-compression in advance.

The rotary compressor according to the present embodiment includes a discharge passage through which refrigerant is discharged from a compression space, and the discharge passage passes between a first discharge guide provided on a main bearing or a sub-bearing and both ends of a roller in an axial direction. It may include two discharge guides, and a third discharge guide provided on a bearing opposite to the bearing having the first discharge guide around the roller and communicating with the first discharge guide through the second discharge guide. Through this, the structure of the cylinder is simplified and easily processed, and the surface pressure between the vane and the cylinder around the discharge hole is lowered and kept constant while reducing the vibration of the vane to reduce wear and vibration noise between the vane and the cylinder. can suppress In addition, the remaining refrigerant in the compression space is reduced by discharging the refrigerant remaining in the residual space, and the effective discharge area is enlarged to quickly discharge the refrigerant to be compressed, thereby reducing the residual refrigerant and improving the compression efficiency. In addition, vane jumping can be suppressed by eliminating the pressure difference on the front surface of the vane, thereby reducing vane or cylinder wear. In addition, as the discharge passage is periodically opened, leakage of the refrigerant during the compression stroke can be suppressed, thereby preventing under-compression from occurring.

In the rotary compressor according to the present embodiment, the first discharge guide may be in periodic communication with the third discharge guide by the second discharge guide when the roller rotates. Through this, it is possible to suppress leakage of the compressed refrigerant while reducing the residual amount of the refrigerant.

The rotary compressor according to the present embodiment may include one first discharge guide part and one third discharge guide part, and a plurality of second discharge guide parts formed at predetermined intervals along the circumferential direction. Through this, the discharge passage for discharging the residual refrigerant may be opened once per rotation of the roller and periodically opened in the residual space communicating with the final compression chamber.

The rotary compressor according to the present embodiment includes: a first guide groove communicating with the first discharge guide part; and a second guide groove having one end communicating with the first guide groove and the other end communicating with the second discharge guide, the second guide groove extending closer to the center of rotation of the roller than the first guide groove. . Through this, the refrigerant in the remaining space can be discharged into the inner space of the casing by periodically passing through the rollers.

In the rotary compressor according to the present embodiment, at least one discharge port is formed in the main bearing or the sub-bearing, and the first guide groove may be formed to have a cross-sectional area larger than or equal to the cross-sectional area of the discharge port where the first guide groove overlaps in the axial direction. . Through this, the refrigerant can be more quickly discharged from the compression space or the remaining refrigerant can be more smoothly discharged.

In the rotary compressor according to the present embodiment, at least one discharge port is formed in the main bearing or the sub-bearing, and the first guide groove is at a rear side relative to the rotation direction of the roller than the discharge port where the first guide groove overlaps in the axial direction. It can be formed to be located in. Through this, it is possible to effectively discharge residual refrigerant remaining in the residual space after the discharge stroke to increase compression efficiency and at the same time suppress vane jumping to suppress vane or cylinder wear.

In the rotary compressor according to the present embodiment, at least one discharge port is formed in the main bearing or the sub-bearing, and the first guide groove is at the front side relative to the rotation direction of the roller than the discharge port where the first guide groove overlaps in the axial direction. It can be formed to be located in. Through this, the effective discharge area of the refrigerant can be expanded so that the refrigerant in the compression chamber can be discharged more quickly, and the amount of refrigerant moving to the residual space can be reduced and the residual amount of refrigerant can be suppressed.

In the rotary compressor according to the present embodiment, the second guide groove may be formed thinner and longer than the first guide groove. Through this, the second guide groove can be formed between the back pressure pockets provided in the bearing, so that the discharge passage passes through the roller and is periodically opened.

In the rotary compressor according to the present embodiment, a plurality of vane slots are formed along the circumferential direction, and second discharge guide units may be provided between each of the vane slots adjacent to each other in the circumferential direction. Through this, the discharge passage is periodically opened to reduce the residual amount of the refrigerant while suppressing leakage of the compressed refrigerant.

In the rotary compressor according to the present embodiment, a plurality of back pressure pockets having different pressures are formed spaced apart along the circumferential direction on one side of the main bearing and one side of the sub bearing facing the rollers in the axial direction, and the third discharge The guide portion may be provided between the plurality of back pressure pockets in a circumferential direction. Through this, the discharge passage is periodically opened to reduce the residual amount of the refrigerant while suppressing leakage of the compressed refrigerant.

In the rotary compressor according to the present embodiment, the main bearing or the sub-bearing may include a discharge muffler accommodating the discharge port, and the third discharge guide may open from the outside of the discharge muffler toward the inner space of the casing. Through this, as the refrigerant is discharged from the outside of the discharge muffler, the increase in the internal pressure of the discharge muffler is suppressed, so that the discharge valve is quickly opened, and at the same time, the vortex phenomenon in the discharge space is suppressed, so that the refrigerant is discharged more quickly from each outlet. can be ejected.

In the rotary compressor according to the present embodiment, a discharge muffler accommodating a discharge port may be provided in a main bearing or a sub-bearing, and the third discharge guide may open toward an inner space of the discharge muffler. Through this, it is possible to easily process the discharge passage by reducing the length of the discharge passage provided in the bearing.

1 is a cross-sectional view showing an embodiment of a vane rotary compressor according to the present invention;
2 is a perspective view showing a part of the compression unit in FIG. 1 by disassembling it;
Figure 3 is a plan view shown by assembling the compression unit in Figure 2;
4 is a perspective view showing a discharge passage by disassembling the compression unit in FIG. 1;
Figure 5 is a perspective view showing a discharge passage by breaking the assembled state of the compression unit in Figure 4;
Figure 6 is a cross-sectional view showing the discharge passage in Figure 5;
Figure 7 is a schematic diagram shown to explain the position of the first discharge guide in the vane rotary compressor according to Figure 1;
8A to 8C are schematic diagrams showing the process of discharging the residual refrigerant through the discharge passage according to the present embodiment;
9 is a plan view showing another embodiment of the discharge passage;
10 is a plan view showing another embodiment of the discharge passage;
11 is a plan view showing another embodiment of the discharge passage
12 is a perspective view showing another embodiment of the discharge passage;
Figure 13 is a cross-sectional view of Figure 12;
14 is an exploded perspective view showing another embodiment of the discharge passage;
15 is an assembled cross-sectional view of FIG. 14;
16 is a schematic view showing a state in which the discharge passage of FIG. 14 is opened;
17 and 18 are a perspective view and a cross-sectional view showing another embodiment of the discharge passage.

Hereinafter, a vane rotary compressor according to the present invention will be described in detail based on an embodiment shown in the accompanying drawings.

The present invention is provided with a vane spring on the roller, which can be equally applied to a vane rotary compressor in which the vane is slidably inserted into the roller. For example, the same can be applied to a vane rotary compressor having an elliptical (hereinafter referred to as an asymmetric elliptical) cylinder having a plurality of curvatures on the inner circumferential surface of the cylinder as well as a vane rotary compressor having a circular cylinder having a single curvature on the inner circumferential surface of the cylinder. can In addition, the same can be applied to a vane rotary compressor in which the vane slot into which the vane is slidably inserted is inclined by a predetermined angle with respect to the radial direction of the roller, as well as a vane rotary compressor in which the vane slot is formed in the radial direction of the roller. . Hereinafter, an example in which the inner circumferential surface of the cylinder of the vane slot has an asymmetric elliptical shape and the vane is inclined with respect to the radial direction of the roller will be described as a representative example.

1 is a cross-sectional view showing an embodiment of a vane rotary compressor according to the present invention, FIG. 2 is a perspective view showing an exploded compression unit in FIG. 1 , and FIG. 3 is a plan view showing an assembled compression unit of FIG. 2 .

Referring to FIG. 1 , the vane rotary compressor according to the present embodiment includes a casing 110, a drive motor 120, and a compression unit 130. The drive motor 120 is installed in the upper inner space 110a of the casing 110 and the compression unit 130 is installed in the lower inner space 110a of the casing 110, respectively, and the drive motor 120 and the compression unit ( 130) is connected to the rotation shaft 123.

The casing 110 is a part constituting the exterior of the compressor, and may be divided into a vertical type or a horizontal type depending on the installation mode of the compressor. The vertical type is a structure in which the drive motor 120 and the compression unit 130 are disposed on both sides along the axial direction, and the horizontal type is a structure in which the drive motor 120 and the compression unit 130 are disposed on both left and right sides. The casing according to this embodiment will be described centering on the bell shape.

The casing 110 includes an intermediate shell 111 formed in a cylindrical shape, a lower shell 112 covering the lower end of the intermediate shell 111, and an upper shell 113 covering the upper end of the intermediate shell 111.

The driving motor 120 and the compression unit 130 are inserted and fixedly coupled to the intermediate shell 111 , and the suction pipe 115 passes through to be directly connected to the compression unit 130 . The lower shell 112 may be sealed and coupled to the lower end of the intermediate shell 111, and a storage space 110b in which oil to be supplied to the compression unit 130 is stored may be formed below the compression unit 130. The upper shell 113 is sealed and coupled to the top of the middle shell 111, and an oil separation space 110c may be formed above the drive motor 120 to separate oil from the refrigerant discharged from the compression unit 130. there is.

The drive motor 120 is a part constituting the transmission part and provides power for driving the compression part 130 . The drive motor 120 includes a stator 121 , a rotor 122 and a rotation shaft 123 .

The stator 121 is fixedly installed inside the casing 110 and may be press-fitted and fixed to the inner circumferential surface of the casing 110 by shrinking or the like. For example, the stator 121 may be fixed by being press-fitted to the inner circumferential surface of the intermediate shell 110a.

The rotor 122 is rotatably inserted into the stator 121, and the rotation shaft 123 may be press-fitted and coupled to the center of the rotor 122. Accordingly, the rotating shaft 123 rotates concentrically with the rotor 122 .

An oil passage 125 is formed in the shape of a hollow hole at the center of the rotation shaft 123, and oil passages 126a and 126b are formed through the outer circumferential surface of the rotation shaft 123 in the middle of the oil passage 125. The oil through-holes 126a and 126b include a first oil through-hole 126a belonging to the range of the main bush portion 1312 to be described later and a second oil through-hole 126b belonging to the range of the sub-bearing portion 1322. The first oil through-hole 126a and the second oil through-hole 126b may be formed one by one or a plurality of each. This embodiment shows an example formed in plurality.

An oil pickup 127 may be installed in the middle or lower end of the oil passage 125 . The oil pickup 127 may be a gear pump, a viscous pump, a centrifugal pump, or the like. This embodiment shows an example in which a centrifugal pump is applied. Accordingly, when the rotary shaft 123 rotates, the oil filled in the oil storage space 110b of the casing 110 is pumped by the oil pickup 127, and the oil is sucked along the oil passage 125 and then sucked up through the second oil passage Oil may be supplied to the sub-bearing surface 1322b of the sub-bush part 1322 through 126b and to the main-bearing surface 1312b of the main bush part 1312 through the first oil passage 126a.

Meanwhile, a roller 134 to be described later may be provided on the rotating shaft 123 . The roller 134 may extend from the rotational shaft 123 as a single body or may be assembled after the rotational shaft 123 and the roller 134 are manufactured separately. In this embodiment, the rotary shaft 123 is inserted into the roller 134 and then assembled. For example, the shaft hole 1341 provided at the center of the roller 134 penetrates in the axial direction, and the shaft hole 1341 The rotary shaft 123 may be press-fitted and coupled or movably coupled in the axial direction. When the rotational shaft 123 is movably coupled to the roller 134 in the axial direction, an anti-rotation unit (not shown) is provided between the rotational shaft 123 and the roller 134 so that the rotational shaft 123 moves the roller 134 ) can be constrained in the circumferential direction.

The compression unit 130 includes a main bearing 131, a sub bearing 132, a cylinder 133, a roller 134, and a plurality of vanes 1351, 1352, and 1353. The main bearing 131 and the sub bearing 132 are provided on both sides of the upper and lower sides of the cylinder 133 to form a compression space (V) together with the cylinder 133, and the roller 134 rotates in the compression space (V). Possibly installed, the vanes 1351, 1352, and 1353 are slidably inserted into the roller 134 to partition the compression space V into a plurality of compression chambers.

Referring to FIGS. 1 to 3 , the main bearing 131 may be fixed to the intermediate shell 111 of the casing 110 . For example, the main bearing 131 may be inserted into and welded to the intermediate shell 111 .

The main bearing 131 may be coupled to the upper end of the cylinder 133 in close contact. Accordingly, the main bearing 131 forms the upper surface of the compression space V, supports the upper surface of the roller 134 in the axial direction and supports the upper half of the rotary shaft 123 in the radial direction.

The main bearing 131 may include a main plate part 1311 and a main bush part 1312 . The main plate part 1311 is coupled to the cylinder 133 by covering the upper side of the cylinder 133, and the main bush part 1312 moves in the axial direction from the center of the main plate part 1311 toward the drive motor 120. It extends to support the upper half of the rotation shaft 123.

The main plate part 1311 is formed in a disk shape, and the outer circumferential surface of the main plate part 1311 may be fixed to the inner circumferential surface of the intermediate shell 111 in close contact. At least one discharge port 1313a, 1313b, and 1313c is formed in the main plate portion 1311, and a plurality of discharge ports 1313a, 1313b, and 1313c are opened and closed on the upper surface of the main plate portion 1311. Two discharge valves 1361, 1362, and 1363 are installed, and the upper side of the main plate part 1311 accommodates the discharge ports 1313a, 1313b, and 1313c and the discharge valves 1361, 1362, and 1363. A discharge muffler 137 having a discharge space (unsigned) may be installed.

Accordingly, as the discharge ports 1313a, 1313b, and 1313c are formed in the main bearing (or sub-bearing) 131 instead of the cylinder 133, the structure of the cylinder 133 is simplified and the cylinder can be easily machined. can In addition, the surface pressure between the front surface of the vane 133 around the discharge ports 1313a, 1313b, and 1313c and the inner circumferential surface of the cylinder 131 facing it is lowered and maintained constant, while the vane 1351 (1352) ) 1353, it is possible to suppress wear and vibration noise between the front surfaces of the vanes 1351, 1352, and 1353 and the inner circumferential surface of the cylinder 133 facing them. The discharge port will be described again later.

Among both sides of the main plate part 1311 in the axial direction, the lower surface of the main plate part 1311 facing the upper surface of the roller 134, that is, the main sliding surface 1311a, has a first main back pressure pocket 1315a and a second main back pressure pocket 1315a. A back pressure pocket 1315b may be formed.

The first main back pressure pocket 1315a and the second main back pressure pocket 1315b may be formed in an arc shape at predetermined intervals along the circumferential direction. The inner circumferential surfaces of the first main back pressure pocket 1315a and the second main back pressure pocket 1315b may be formed in a circular shape, but the outer circumferential surfaces may be formed in an elliptical shape in consideration of a vane slot to be described later.

The first main back pressure pocket 1315a and the second main back pressure pocket 1315b may be formed within the outer diameter range of the roller 134 . Accordingly, the first main back pressure pocket 1315a and the second main back pressure pocket 1315b may be separated from the compression space V. However, the first main back pressure pocket 1315a and the second main back pressure pocket 1315b provide a separate seal between the main sliding surface 1311a, which is the lower surface of the main plate part 1311, and the upper surface of the roller 134 facing it. Unless a member is provided, fine communication can be achieved through the gap between both sides.

The first main back pressure pocket 1315a forms a lower pressure than the second main back pressure pocket 1315b, for example, an intermediate pressure between suction pressure and discharge pressure. In the first main back pressure pocket 1315a, oil (refrigerant oil) passes through a fine passage between a first main bearing protrusion 1316a and the upper surface of the roller 134 to be introduced into the first main back pressure pocket 1315a. can The first main back pressure pocket 1315a may be formed within a range of a compression chamber forming an intermediate pressure in the compression space V. Accordingly, the first main back pressure pocket 1315a maintains an intermediate pressure.

The second main back pressure pocket 1315b forms a higher pressure than the first main back pressure pocket 1315a, for example, a discharge pressure or an intermediate pressure between a suction pressure close to the discharge pressure and a discharge pressure. In the second main back pressure pocket 1315b, oil flowing into the main bearing hole 1312a of the main bearing 1312 through the first oil passage 126a may flow into the second main back pressure pocket 1315b. The second main back pressure pocket 1315b may be formed within the range of the compression chamber forming the discharge pressure in the compression space V. Accordingly, the second main back pressure pocket 1315b maintains the discharge pressure.

In addition, on the inner circumferences of the first main back pressure pocket 1315a and the second main back pressure pocket 1315b, the first main bearing protrusion 1316a and the second main bearing protrusion 1316b respectively form the main bearings of the main bush 1312. It may be formed extending from the face 1312b. Accordingly, the first main back pressure pocket 1315a and the second main back pressure pocket 1315b are sealed against the outside, and the rotation shaft 123 can be stably supported.

The first main bearing protrusion 1316a and the second main bearing protrusion 1316b may be formed at the same height or may be formed at different heights.

For example, when the first main bearing protrusion 1316a and the second main bearing protrusion 1316b are formed at the same height, the second main bearing protrusion 1316b is formed on the end surface of the second main bearing protrusion 1316b. An oil communication groove (not shown) or an oil communication hole (not shown) may be formed so that the inner circumferential surface and the outer circumferential surface communicate with each other. Accordingly, high-pressure oil (refrigerant oil) flowing into the inner side of the main bearing surface 1312b is introduced into the second main back pressure pocket 1315b through an oil communication groove (not shown) or an oil communication hole (not shown). can

On the other hand, when the first main bearing protrusion 1316a and the second main bearing protrusion 1316b are formed at different heights, the height of the second main bearing protrusion 1316b is greater than the height of the first main bearing protrusion 1316a. can be made low. Accordingly, high-pressure oil (refrigerant oil) flowing into the main bearing hole 1312a can pass over the second main bearing protrusion 1316b and flow into the second main back pressure pocket 1315b.

In addition, a third discharge guide portion 143 forming a part of a residual refrigerant discharge passage 140 to be described later may be formed on the main sliding surface 1311a. The third discharge guide 143 may be formed between the first main back pressure pocket 1315a and the second main back pressure pocket 1315b. The first end 143a of the third discharge guide 143 is formed to periodically communicate with the second end 142b of the second discharge guide 142 of the roller 134 to be described later, and the third discharge guide The second end 143b of the portion 143 may pass through the main bush portion 1312 to be described later in the axial direction and open toward the inner space 110a of the casing 110 . The third discharge guide part 143 will be described again together with the residual refrigerant discharge passage 140 later.

Meanwhile, the main bush portion 1312 may be formed in a hollow bush shape, and a first oil groove 1312c may be formed on an inner circumferential surface of the main bearing hole 1312a constituting the inner circumferential surface of the main bush portion 1312 . The first oil groove 1312c may be formed in a straight line or an oblique line between upper and lower ends of the main bush portion 1312 to communicate with the first oil through hole 126a.

Referring to FIGS. 1 to 3 , the sub-bearing 132 may be closely coupled to the lower end of the cylinder 133 . Accordingly, the sub-bearing 132 forms the lower surface of the compression space V, supports the lower surface of the roller 134 in the axial direction and supports the lower half of the rotary shaft 123 in the radial direction.

The sub-bearing 132 may include a sub-plate part 1321 and a sub-bush part 1322 . The sub-plate portion 1321 is coupled to the cylinder 133 by covering the lower side of the cylinder 133, and the sub-bush portion 1322 extends from the center of the sub-plate portion 1321 toward the lower shell 112 in the axial direction. It extends to support the lower half of the rotation shaft 123.

Like the main plate part 1311, the sub-plate part 1321 is formed in a disk shape, and the outer circumferential surface of the sub-plate part 1321 may be spaced apart from the inner circumferential surface of the intermediate shell 111.

A first sub back pressure pocket 1325a and a second sub back pressure pocket 1325a are provided on the upper surface of the sub plate part 1321 facing the lower surface of the roller 134 and on the sub sliding surface 1321a of both sides of the sub plate part 1321 in the axial direction. A pocket 1325b may be formed.

The first sub back pressure pocket 1325a and the second sub back pressure pocket 1325b are formed symmetrically around the roller 134 in the first main back pressure pocket 1315a and the second main back pressure pocket 1315b, respectively. can

For example, the first sub back pressure pocket 1325a may be formed symmetrically with the first main back pressure pocket 1315a, and the second sub back pressure pocket 1325b may be formed symmetrically with the second main back pressure pocket 1315b. Accordingly, the first sub-bearing protrusion 1326a may be formed on the inner circumferential side of the first sub back pressure pocket 1325a, and the second sub-bearing protrusion 1326b may be formed on the inner circumferential side of the second sub back pressure pocket 1325b.

For the first sub back pressure pocket 1325a, the second sub back pressure pocket 1325b, the first sub bearing protrusion 1326a and the second sub bearing protrusion 1326b, the first main back pressure pocket 1315a and the second main back pressure pocket 1315a The pocket 1315b, the first main bearing protrusion 1316a and the second main bearing protrusion 1316b are described instead.

However, in some cases, the first sub back pressure pocket 1325a and the second sub back pressure pocket 1325b are centered around the roller 134 in the first main back pressure pocket 1315a and the second main back pressure pocket 1315b, respectively. It can be formed asymmetrically. For example, the first sub back pressure pocket 1325a and the second sub back pressure pocket 1325b may be formed deeper than the first main back pressure pocket 1315a and the second main back pressure pocket 1315b.

In addition, a first discharge guide 141 forming a part of a residual refrigerant discharge passage 140 to be described later may be formed on the sub-sliding surface 1321a. The first discharge guide 141 may be formed between the first sub back pressure pocket 1325a and the second sub back pressure pocket 1325b. One side of the first discharge guide 141 communicates with the compression space V, more precisely, the residual space S, and the other side of the first discharge guide 141 is provided on the roller 134 to be described later. 2 may be formed to communicate with the discharge guide 142 periodically. The first discharge guide part 141 will be described again together with the residual refrigerant discharge passage 140 later.

Meanwhile, the sub-bush portion 1322 may be formed in a hollow bush shape, and an oil groove 1322c may be formed on an inner circumferential surface of the sub-bearing hole 1322a constituting the inner circumferential surface of the sub-bush portion 1322 . The oil groove 1322c may be formed in a straight line or an oblique line between the upper and lower ends of the sub bush 1322 and communicate with the second oil passage 126b of the rotation shaft 123 .

Although not shown in the drawings, the back pressure pockets [(1315a) (1315b)] [(1325a) (1325b)] may be formed only on either side of the main bearing 131 or the sub-bearing 132.

Meanwhile, the discharge port 1313 may be formed in the main bearing 131 as described above. However, the discharge port 1313 may be formed in the sub-bearing 132 or may be formed in the main bearing 131 and the sub-bearing 132, respectively, or may be formed penetrating between the inner and outer circumferences of the cylinder 133. This embodiment will be described based on an example in which the discharge port 1313 is formed in the main bearing 131.

Only one discharge port 1313 may be formed. However, in the discharge port 1313 according to the present embodiment, a plurality of discharge ports 1313a, 1313b, and 1313c may be formed at predetermined intervals along the direction of compression (or the direction of rotation of the roller).

In general, in the vane rotary compressor, as the roller 134 is disposed eccentrically with respect to the compression space V, the contact point ( P) is generated, and the discharge port 1313 is formed to be adjacent to the contact point P on the opposite side of the suction port 1331 with the contact point P as the center. Accordingly, as the compression space V approaches the contact point P, the distance between the inner circumferential surface 1332 of the cylinder 133 and the outer circumferential surface 1342 of the roller 134 greatly narrows, so that the area of the discharge port 1313 is secured. becomes difficult

Accordingly, the discharge port 1313 according to the present embodiment is divided into a plurality of discharge ports 1313a, 1313b, and 1313c having a small inner diameter, and the plurality of discharge ports 1313a, 1313b, and 1313c are formed in a circumferential direction, that is, a roller ( 134) may be arranged at predetermined intervals along the rotation direction.

In addition, the plurality of outlets 1313a, 1313b, and 1313c may be formed individually, but may be formed in pairs as in the present embodiment. For example, the discharge ports 1313 may be arranged in the order of the first discharge port 1313a, the second discharge port 1313b, and the third discharge port 1313c from the nearest discharge port in the proximity portion 1332a.

Intervals between the respective discharge ports 1313a, 1313b, and 1313c may be substantially the same. For example, the first interval between the rear end of the first outlet 1313a and the front end of the second outlet 1313b is approximately equal to the second interval between the rear end of the second outlet 1313b and the front end of the third outlet 1313c. can be formed in the same way.

In addition, the distance from the front end to the rear end of the discharge port 1313, that is, the arc length of the discharge port 1313 may be formed to be approximately the same as the arc length of each compression chamber V1, V2, and V3. For example, the arc length between the front end of the first discharge port 1313a and the rear end of the third discharge port 1313b is the distance between the preceding vane and the following vane, that is, each compression chamber V1, V2, and V3. It may be formed approximately similar to the arc length.

However, in some cases, the arc length between the front end of the first discharge port 1313a and the rear end of the third discharge port 1313b is the distance between the preceding vane and the following vane, that is, each compression chamber V1, V2 ( It may be formed larger than the arc length of V3). In this case, as at least one compression chamber (V1) (V2) (V3) is located within the circumferential range of the discharge port 1313, continuous discharge is possible, and through this, overcompression or / and pressure pulsation can be suppressed. there is.

Although not shown in the drawings, when the vane slots 1343a, 1343b, and 1343c to be described later are formed at equal intervals, the circumferential lengths of each compression chamber V1, V2, and V3 are formed differently, and one A plurality of discharge ports may communicate with the compression chamber, or a plurality of compression chambers may communicate with one discharge port.

In addition, the plurality of discharge ports 1313a, 1313b, and 1313c may be opened and closed by respective discharge valves 1361, 1362, and 1363 described above. Each of the discharge valves 1361, 1362, and 1363 may be configured as a cantilever type reed valve in which one end is a fixed end and the other end is a free end. Since each of these discharge valves 1361, 1362, and 1363 is widely known in a conventional rotary compressor, a detailed description thereof will be omitted.

1 to 3 , the cylinder 133 according to the present embodiment may come into close contact with the lower surface of the main bearing 131 and be bolted together with the sub bearing 132 to the main bearing 131 . Accordingly, the cylinder 133 may be fixedly coupled to the casing 110 by the main bearing 131 .

Cylinder 133 may be formed in an annular shape having an empty space portion to form a compression space (V) in the center. The empty space is sealed by the main bearing 131 and the sub-bearing 132 to form the compression space V described above, and a roller 134 to be described later may be rotatably coupled to the compression space V.

The cylinder 133 may be formed by penetrating the inlet 1331 from the outer circumferential surface to the inner circumferential surface. However, the inlet may be formed through the main bearing 131 or the sub-bearing 132.

The inlet 1331 may be formed on one side in the circumferential direction around a contact point P, which will be described later. The discharge port 1313 described above may be formed on the main bearing 131 on the other side in the circumferential direction opposite to the suction port 1331 with the contact point P as the center.

The inner circumferential surface 1332 of the cylinder 133 may be formed in an oval shape. The inner circumferential surface 1332 of the cylinder 133 according to the present embodiment may be formed into an asymmetrical elliptical shape by combining a plurality of ellipses, for example, four ellipses having different long and short ratios to have two origins.

Specifically, the inner circumferential surface 1332 of the cylinder 133 according to this embodiment refers to the center of the roller 134 or the center of rotation of the roller 134 (axis center or outer diameter center of the cylinder) (Or) as a first origin point, which will be described later. (O), it may be formed to have a second origin point (O′) biased toward the contact point (P) with respect to the first origin point (O).

The X-Y plane formed around the first origin point O forms the third quadrant Q3 and the fourth quadrant Q4, and the X-Y plane formed around the second origin point O' forms the first quadrant ( Q1) and the second quadrant Q2 are formed. The third quadrant Q3 is formed by the third ellipse, the fourth quadrant Q4 is formed by the fourth ellipse, the first quadrant Q1 is formed by the first ellipse, and the second quadrant Q2 is formed by the second ellipse. Each is formed by two ellipses.

In addition, the inner circumferential surface 1332 of the cylinder 133 according to the present embodiment may include a proximal portion 1332a, a circular portion 1332b, and a curved portion 1332c. The proximal part 1332a is the part closest to the outer circumferential surface of the roller 134 (or the center of rotation of the roller) 1341, and the circular contact part 1332b is located farthest from the outer circumferential surface 1342 of the roller 134. portion, and the curved portion 1332c is a portion connecting the proximity portion 1332a and the distal portion 1332b.

The proximity portion 1332a may also be defined as a contact point P, and the previously described first and fourth quadrants Q1 and Q4 may be divided based on the proximity portion 1332a. A suction port 1331 may be formed in the first quadrant Q1 and a discharge port 1313 may be formed on both sides of the proximity portion 1332a as the center, respectively. Accordingly, when the vanes 1351, 1352, and 1353 pass the contact point P, the compression surface in the rotational direction of the rollers 1351, 1352, and 1353 receives a low pressure suction pressure, but the opposite side, the compression back surface, receives a high pressure. discharge pressure. Then, in the process of the roller 134 passing through the contact point P, the front surfaces 1351a, 1352a, and 1353a of each vane 1351, 1352, and 1353 in contact with the inner circumferential surface of the cylinder 133 and the back pressure chamber ( The largest variable pressure is received between the rear end surfaces 1351b, 1352b, and 1353b of each vane 1351, 1352, and 1353 toward 1344a, 1344b, and 1344c, which causes the vane 1351 to The shaking phenomenon of (1352) (1353) may occur greatly.

1 to 3, the roller 134 according to the present embodiment is rotatably provided in the compression space V of the cylinder 133, and the roller 134 includes a plurality of vanes 1351 (which will be described later) 1352 and 1353 may be inserted at predetermined intervals along the circumferential direction. Accordingly, compression chambers corresponding to the number of the plurality of vanes 1351, 1352, and 1353 may be partitioned and formed in the compression space V. In this embodiment, the plurality of vanes 1351, 1352, and 1353 are composed of three, and the compression space V is mainly described as an example in which three compression chambers V1, V2, and V3 are partitioned.

As described above, the roller 134 may extend from the rotating shaft 123 as a single body or may be manufactured separately from the rotating shaft 123 and then assembled. In this embodiment, an example in which the roller 134 and the rotation shaft 123 are post-assembled will be mainly described.

However, even when the roller 134 extends to the rotational shaft 123 as a single body, the rotational shaft 123 and the roller 134 may be formed similarly to the present embodiment, and the basic operational effect thereof is almost the same as that of the present embodiment. can be similar However, when the roller 134 is post-assembled to the rotating shaft 123 as in this embodiment, the roller 134 may be formed of a material different from that of the rotating shaft 123, for example, a hard material lighter than the rotating shaft 123. . In this case, it is possible to facilitate the processing of the roller 134 and increase the efficiency of the compressor by lowering the weight of the rotating body including the roller 134.

The roller 134 according to this embodiment may be formed as a single body, that is, an integral roller made of one roller body (unsigned). However, the roller 134 need not necessarily be formed as an integral roller. For example, the roller 134 may be formed as a separable roller separated into a plurality of roller bodies (unsigned). This will be described later in another embodiment, and in this embodiment, the single-piece roller 134 will be mainly described.

Referring to FIGS. 1 to 3 , the roller 134 according to this embodiment may be formed in an annular shape with a shaft hole 1341 provided at its center. For example, the roller 134 may have an inner circumferential surface and an outer circumferential surface, and the inner circumferential surface and the outer circumferential surface of the roller 134 may each be formed in a circular shape. However, while the inner circumferential surface of the roller 134 is formed as a continuous surface, the outer circumferential surface of the roller 134 is provided with opening surfaces of the vane slots 1343a, 1343b, and 1343c to be described later, so that the vane slots 1343a, 1343b ( 1343c) may be formed as discontinuous surfaces.

In addition, the rotation center Or of the roller 134 is located coaxially with the axis center (unsigned) of the rotation shaft 123, and the roller 134 rotates concentrically with the rotation shaft 123. However, as described above, as the inner circumferential surface 1332 of the cylinder 133 is formed in an asymmetric elliptical shape tilted in a specific direction, the rotation center Or of the roller 134 is relative to the outer diameter center Oc of the cylinder 133. It can be placed eccentrically. Accordingly, one side of the outer circumferential surface 1341b of the roller 134 almost contacts the inner circumferential surface 1332 of the cylinder 133, more precisely, the adjacent portion 1332a to form a contact point P.

As described above, the contact point P may be formed at the proximal portion 1332a. Accordingly, a virtual line passing through the contact point P may correspond to a minor axis of an elliptic curve forming the inner circumferential surface 1332 of the cylinder 133 .

A plurality of vane slots 1343a, 1343b, and 1343c are formed in the roller 134, and vanes 1351, 1352, and 1353, which will be described later, are respectively formed in each vane slot 1343a, 1343b, and 1343c. It can be slid in and engaged. The plurality of vane slots 1343a, 1343b, and 1343c are formed at predetermined intervals along the circumferential direction, and the outer circumferential surface 1342 of the roller 134 is formed with an opening surface that is opened in the radial direction. The opposite inner end may be provided with back pressure chambers 1344a, 1344b, and 1344c, which will be described later, and formed in a radially blocked shape.

The plurality of vane slots 1343a, 1343b, and 1343c are defined as a first vane slot 1343a, a second vane slot 1343b, and a third vane slot 1343c along the direction of compression (roller rotation direction). In addition, the first vane slot 1343a, the second vane slot 1343b, and the third vane slot 1343c may be equally formed at equal intervals or unequal intervals along the circumferential direction.

For example, each of the vane slots 1343a, 1343b, and 1343c is inclined by a predetermined angle with respect to the radial direction, so that the lengths of the vanes 1351, 1352, and 1353 can be sufficiently secured. Accordingly, when the inner circumferential surface 1332 of the cylinder 133 is formed in an asymmetric elliptical shape, even if the distance from the outer circumferential surface 1342 of the roller 134 to the inner circumferential surface 1332 of the cylinder 133 increases, the vane 1351 (1352) (1353) can be suppressed from being separated from the vane slots (1343a) (1343b) (1343c), and through this, the design freedom for the inner circumferential surface (1332) of the cylinder 133 as well as for the roller 134 Design freedom can be increased.

The direction in which the vane slots 1343a, 1343b, and 1343c are inclined is opposite to the rotational direction of the roller 134, that is, each vane 1351, 1352, and 1353 in contact with the inner circumferential surface 1332 of the cylinder 133. It may be preferable that the front surfaces 1351a, 1352a, and 1353a of the inclination toward the direction of rotation of the roller 134 can pull the compression start angle toward the direction of rotation of the roller 134 so that compression can start quickly. .

Each of the back pressure chambers 1344a, 1344b, and 1344c may be formed to communicate with inner ends of the respective vane slots 1343a, 1343b, and 1343c. Each of the back pressure chambers 1344a, 1344b, and 1344c is formed on the rear side of each vane 1351, 1352, and 1353, that is, the rear end surface 1351c, 1352c, and 1353c of the vane 1351, 1352, and 1353. A space in which discharge pressure or intermediate pressure oil (or refrigerant) is accommodated, and each vane (1351) (1352) ) 1353 may be pressed toward the inner circumferential surface of the cylinder 133. Hereinafter, the direction toward the inner circumferential surface of the cylinder based on the motion direction of the vane can be defined as forward, and the opposite side as rear.

Although not shown in the drawings, the plurality of vane slots 1343a, 1343b, and 1343c may be radially formed with respect to the rotational center Or of the roller 134, that is, radially. The action effect according to this is similar to that of the embodiment to be described later in which the plurality of vane slots 1343a, 1343b, and 1343c are formed inclined with respect to the rotation center Or of the roller 134. replaced by an explanation of

A second discharge guide part 142 forming a part of a residual refrigerant discharge passage 140 to be described later may be formed on the roller 134 . A plurality of second discharge guides 142 may be formed between vane slots [(1343a, 1343b) (1343b, 1343c) (1343c, 1343a)] adjacent to each other in the circumferential direction. The first end 142a of the second discharge guide 142 is formed to periodically communicate with the second end 1412b of the second guide groove 1412 of the first discharge guide 141, and The second end 142b of the guide part 142 may be formed to periodically communicate with the first end 143a of the third discharge guide part 143 to be described later. The second discharge guide part 142 will be described again together with the residual refrigerant discharge passage 140 later.

Meanwhile, the back pressure chambers 1344a, 1344b, and 1344c may be formed to be sealed by the main bearing 131 and the sub-bearing 132, respectively. The back pressure chambers 1344a, 1344b, and 1344c may communicate independently with each of the back pressure pockets [(1315a) (1315b)] [(1325a) (1325b)], and the back pressure pockets [(1315a) (1315b)] ][(1325a)(1325b)] may be formed to communicate with each other.

1 to 3, the plurality of vanes 1351, 1352, and 1353 according to the present embodiment may be slidably inserted into respective vane slots 1343a, 1343b, and 1343c. Accordingly, the plurality of vanes 1351, 1352, and 1353 may be formed in substantially the same shape as the respective vane slots 1343a, 1343b, and 1343c.

For example, the plurality of vanes 1351, 1352, and 1353 may be defined as a first vane 1351, a second vane 1352, and a third vane 1353 along the rotational direction of the roller 134. there is. The first vane 1351 is inserted into the first vane slot 1343a, the second vane 1352 is inserted into the second vane slot 1343b, and the third vane 1353 is inserted into the third vane slot 1343c, respectively. can

The plurality of vanes 1351, 1352, and 1353 may be formed in substantially the same shape. For example, each of the plurality of vanes 1351, 1352, and 1353 is formed in a substantially rectangular parallelepiped, and the front surface 1351a of the vanes 1351, 1352, and 1353 in contact with the inner circumferential surface 1332 of the cylinder 133 (1352a) (1353a) may be formed as a curved surface along the circumferential direction. Accordingly, the front surfaces 1351a, 1352a, and 1353a of the vanes 1351, 1352, and 1353 come into line contact with the inner circumferential surface 1332 of the cylinder 133, thereby reducing friction loss.

Meanwhile, the sub-bearing 132, the roller 134, and the main bearing 131 communicate with the residual space (S) to discharge the refrigerant remaining in the residual space (S) to the inner space (110a) of the casing (110). A residual refrigerant discharge passage 140 may be formed.

The residual refrigerant discharge passage 140 includes a first discharge guide 141 provided on the sub-bearing 132, a second discharge guide 142 provided on the roller, and a third discharge guide provided on the main bearing 131. It includes a portion 143, and the first discharge guide 141, the second discharge guide 142, and the third discharge guide 143 may be formed to continuously communicate. Accordingly, the refrigerant remaining in the residual space (S) is directed to the inner space (110a) of the casing (110) through the first discharge guide part (141), the second discharge guide part (142), and the third discharge guide part (143). may be discharged. The residual refrigerant discharge passage 140 will be described again later.

In the vane rotary compressor equipped with the hybrid cylinder as described above, when power is applied to the drive motor 120, the rotor 122 of the drive motor 120 and the rotation shaft 123 coupled to the rotor 122 rotate. And, the roller 134 coupled to or integrally formed with the rotating shaft 123 rotates together with the rotating shaft 123.

Then, the plurality of vanes 1351, 1352, and 1353 are affected by the centrifugal force generated by the rotation of the roller 134 and the rear end surfaces 1351b, 1351b, and 1351c of the vanes 1351, 1352, and 1353. By the back pressure force of the back pressure chambers 1344a, 1344b, and 1344c supporting the vane slots 1343a, 1343b, and 1343c, the vanes come into contact with the inner circumferential surface 1332 of the cylinder 133.

Then, the compression space V of the cylinder 133 is formed by the plurality of vanes 1351, 1352, and 1353, and the compression chamber (suction chamber or discharge chamber) as many as the number of the plurality of vanes 1351, 1352, and 1353 It is divided into (V1) (V2) (V3), and each compression chamber (V1) (V2) (V3) moves along the rotation of the roller 134 while moving along the inner circumference 1332 of the cylinder 133 The volume is varied by the shape and the eccentricity of the roller 134, and the refrigerant sucked into each of the compression chambers V1, V2, and V3 follows the roller 134 and the vanes 1351, 1352, and 1353. A series of processes of being compressed while moving and discharged into the inner space of the casing 110 are repeated.

At this time, since the distance between the inner circumferential surface 1332 of the cylinder 133 and the outer circumferential surface 1322 of the roller 134 rapidly narrows as it approaches the contact point P, the third discharge port 1313c, which is the final discharge port, is the contact point ( It is formed at a predetermined interval in the circumferential direction from P). Accordingly, a residual space (S) is formed between the third discharge port (1313c) and the contact point (P), and undischarged refrigerant that has not been discharged even through the third discharge port (1313c) remains in the residual space (S). As described above, this may cause overcompression in the residual space (S) to reduce the efficiency of the compressor.

Accordingly, in this embodiment, one end communicates between the third discharge port 1313c and the contact point P, and the other end communicates with the inner space 110a of the casing 110. The residual refrigerant discharge passage (hereinafter, the discharge passage) ( 140) may be further formed. Accordingly, the refrigerant remaining in the residual space (S) is discharged to the inner space (110a) of the casing 110 to suppress or minimize the refrigerant remaining in the residual space (S), thereby reducing the efficiency of the compressor due to overcompression of the refrigerant can be prevented from becoming

In the discharge passage 140 according to the present embodiment, the inlet of the discharge passage 140 is in the bearing not provided with a discharge port, and the outlet of the discharge passage 140 is in the bearing provided with the discharge port with the roller 134 interposed therebetween. An intermediate passage may be formed in the roller 134 to periodically or intermittently communicate between the inlet of the discharge passage 140 and the outlet of the discharge passage 140 . Accordingly, the refrigerant remaining in the residual space (S) is the inlet of the discharge passage 140, the middle passage of the discharge passage 140, and the discharge passage 140 when the inlet and outlet of the discharge passage 140 communicate with each other through the intermediate passage. ) It can be discharged to the inner space (110a) of the casing (110) passing through the outlet in turn.

For example, when the discharge ports 1313a, 1313b, 1313c and the discharge muffler 137 are provided in the main bearing 131, the inlet of the discharge passage 140 is formed in the sub-bearing 132, and the discharge passage The outlet of 140 may be formed in the main bearing 131. However, when the discharge port and the discharge muffler are provided in the sub-bearing 132, the inlet of the discharge passage 140 may be formed in the main bearing 131, and the outlet of the discharge passage 140 may be formed in the sub-bearing 132. there is.

As described above, even when the inlet and outlet of the discharge passage 140 are formed in opposite bearings, the basic shape of the discharge passage 140 or the effect thereof may be the same. Hereinafter, an example in which the inlet of the discharge passage 140 is formed in the sub bearing 132 and the outlet of the discharge passage 140 is formed in the main bearing 131 will be described.

4 is a perspective view showing a discharge passage by disassembling the compression unit in FIG. 1, FIG. 5 is a perspective view showing a discharge passage by breaking the assembled state of the compression unit in FIG. 4, and FIG. 6 is a cross-sectional view showing the discharge passage in FIG. , Figure 7 is a schematic diagram shown to explain the position of the first discharge guide in the vane rotary compressor according to Figure 1.

Referring back to FIG. 1 , in the rotary compressor according to the present embodiment, discharge ports 1313a, 1313b, and 1313c are axially penetrated through the main plate portion 1311 of the main bearing 131, and the main plate Discharge valves 1361, 1362, and 1363 for opening and closing the discharge ports 1313a, 1313b, and 1313c are provided on one side of the part 1311, that is, on the side opposite to the main sliding surface 1311a, and the main bearing ( A discharge muffler 137 accommodating discharge ports 1313a, 1313b, and 1313c and discharge valves (!361, 1362, and 1363) may be provided on an outer surface of 131.

Referring to FIGS. 4 to 6 , the discharge muffler 137 may include a muffler fixing portion 1371 and a discharge space portion 1372 .

The muffler fixing part 1371 is formed in a flange shape to be fastened to the outer surface of the main bearing 131, and the discharge space part 1372 extends from the inner circumferential surface of the muffler fixing part 1371 to be formed in a substantially cylindrical shape. .

For example, the outer diameter of the muffler fixing part 1371 is formed smaller than the outer diameter of the main plate part 1311, and a plurality of bolt holes (unsigned) are formed along the circumferential direction so that the main bearing 131 has a cylinder 133 ) and can be bolted together with the sub-bearing 132.

The discharge space portion 1372 may be formed in a substantially cylindrical shape by being bent to protrude from the muffler fixing portion 1371 in the axial direction. Accordingly, the inner surface of the discharge space portion 1372 is spaced apart from the outer surface of the main plate portion 1311 to form a discharge space 1372a, and the discharge ports 1313a, 1313b, and 1313c described above are formed in the discharge space 1372a. ) and discharge valves 1361, 1362, and 1363 may be accommodated.

The height H1 of the discharge space 1372 based on the upper surface of the main plate 1311 is lower than the height H2 of the main bush 1312, and the center of the discharge space 1372 has a bearing. A through hole 1372b may be formed. Accordingly, the discharge space 1372 may be inserted into and coupled to the main bush 1312 of the main bearing 131 .

The inner circumferential surface of the bearing through-hole 1372b is spaced apart from the outer circumferential surface of the main bush portion 1312 by a predetermined interval, and the inner circumferential surface of the bearing through-hole 1372b has a discharge interval D between the outer circumferential surface of the main bush portion 1312. can be formed Accordingly, the refrigerant compressed in the compression chambers V1, V2, and V3 passes through the discharge ports 1313a, 1313b, and 1313c and is discharged to the discharge space 1372a of the discharge muffler 137, and the refrigerant is discharged into the discharge muffler ( 137) is discharged into the inner space 110a of the casing 110 through the discharge interval D between the inner circumferential surface and the outer circumferential surface of the main boss 1312. At this time, the pulsation pressure of the refrigerant may be reduced in the discharge space 1372a.

4 to 6, the discharge passage 140 according to the present embodiment may include a first discharge guide 141, a second discharge guide 142 and a third discharge guide 143. there is. The first discharge guide 141 may be formed on the sub bearing 132, the second discharge guide 142 may be formed on the roller 134, and the third discharge guide 143 may be formed on the main bearing 131, respectively. there is.

For example, the first discharge guide unit 141 according to the present embodiment may include a first guide groove 1411 and a second guide groove 1412 . The first guide groove 1411 may communicate with the compression space V, more precisely the residual space S, and the second guide groove 1412 may communicate with the second discharge guide 142.

The first guide groove 1411 may be formed in substantially the same shape as the third discharge port 1313c, which is the final discharge port. For example, the first guide groove 1411 may be formed in a circular cross-section.

The first guide groove 1411 may be formed at a position where at least a portion of the third discharge port 1313c may overlap in the axial direction. For example, when the third discharge port 1313c is formed of a pair of two as shown in FIG. 3, the first guide groove 1411 is a third discharge port relatively adjacent to the contact point (hereinafter, the third discharge port on the rear side) 1313c2 It may be formed at a position where at least a part may overlap with.

Referring to FIG. 7 , the first guide groove 1411 is formed to be positioned on the same axis as the rear third outlet 1313c2 or closer to the contact point P than the rear third outlet 1313c2. It can be.

For example, when the end of the third discharge port 1313c2 on the rear side is formed at an angle of about 5° or more, which is the minimum sealing distance (or sealing angle) (α) from the contact point P, the first guide groove ( 1411) may be formed to be more eccentric toward the contact point P than the rear-side third discharge port 1313c2. In this case, it is preferable that the first guide groove 1411 is formed at a position widened by about 5° or more from the contact point P so as to secure the minimum sealing distance α described above. Accordingly, it is possible to suppress the high-pressure refrigerant from flowing into the suction side beyond the contact point P by the first guide groove 1411 .

On the other hand, when the end of the rear side third discharge port 1313c2 is formed at a position that is approximately 5°, which is the minimum sealing distance α from the contact point P, the first guide groove 1411 is the rear side third discharge port ( 1313c2) and may be formed to be located on the substantially coaxial line. Even in this case, it is possible to suppress the high-pressure refrigerant from flowing into the suction side beyond the contact point P by the first guide groove 1411 .

In addition, the first guide groove 1411 may be formed so that approximately 50% or more of the total area of the first guide groove 1411 overlaps the rear third outlet 1313c2 in the axial direction. Accordingly, the area where the first guide groove 1411 overlaps with the residual space S described above in the axial direction is widened, so that residual refrigerant can be effectively discharged.

According to this embodiment, the discharge passage arc angle β may be greater than or equal to the vane seam angle θ, and preferably, the discharge passage arc arc angle β may be greater than the vane seam angle θ. In FIG. 7, the discharge passage arc angle β is shown to be smaller than the vane seam angle θ, but when the first guide groove 1411 is formed in a long rectangular shape in the circumferential direction, the discharge passage arc arc angle β is the vane seam angle ( It can be formed greater than or equal to θ).

Here, the arc angle β of the discharge passageway is both ends from the start end of the first discharge port 1313a forming the first discharge port to the end of the first guide groove 1411 located behind the third discharge port 1313c forming the final discharge port. defined as the circular arc angle between, and the vane angle (θ) is the case where the three vanes 1351, 1352, and 1353 are arranged at equal intervals along the circumferential direction of the roller 134, both adjacent vanes 1351 and 1352 ) (1352, 1353) (1353c, 1351).

In this case, the vane angle θ may be 120°, and the arc angle β of the discharge passage may be greater than or equal to about 120°, preferably greater than 120°. Accordingly, the discharge passage including the discharge port and the discharge passage 140 may extend to the circumferential range of the compression chamber or outside the circumferential range of the compression chamber. Then, the length of the discharge stroke for the refrigerant in the compression chamber can be secured longer than the length of the compression stroke, and through this, the remaining space (S) remaining after the discharge stroke in the compression chamber or adjacent to the contact point (P) It is possible to minimize the amount of compressed refrigerant remaining in the In addition, as the arc length of the discharge passage is formed equal to or longer than the arc length of the compression chamber, continuous discharge is possible and pressure pulsation can be reduced.

In addition, the first guide groove 1411 may have a cross-sectional area larger than or equal to the cross-sectional area of the third discharge port 1313c2 on the rear side. Accordingly, the area of the first guide groove 1411 overlapping with the residual refrigerant is enlarged so that the residual refrigerant can be discharged more effectively. However, the cross-sectional area of the first guide groove 1411 may be smaller than that of the third discharge port 1313c2 on the rear side.

Although not shown in the drawing, the first guide groove 1411 may be formed in various shapes. For example, in FIGS. 4 to 8, only one first guide groove 1411 is formed, but in some cases, the first guide groove 1411 is formed in a pair like the third discharge port, but is formed to communicate with each other, or Alternatively, it may be formed in a single long groove shape. In this case, the first guide groove 1411 is elongated in the circumferential direction so that residual refrigerant can be discharged more effectively.

4 to 6, the first end 1412a of the second guide groove 1412 communicates with the first guide groove 1411, and the second end 1412b of the second guide groove 1412 It may communicate with the second discharge guide part 142 . For example, the second guide groove 1412 may be formed in a rectangular shape extending long in the radial direction.

Specifically, the first end 1412a of the second guide groove 1412 may be located outside in the radial direction, and the second end 1412b of the second guide groove 1412 may be located inside in the radial direction. Accordingly, the second end 1412b of the second guide groove 1412 may be positioned closer to the rotation center Or of the roller 134 than the first guide groove 1411 .

The cross-sectional area (or width) of the second guide groove 1412 may be smaller than the inner diameter of the first guide groove 1411 . For example, the second guide groove 1412 may be thinner and longer than the first guide groove 1411 . Accordingly, a part of the second guide groove 1412 may be formed between the first sub back pressure pocket 1325a and the second sub back pressure pocket 1325b. For example, the first end 1412a of the second guide groove 1412 is formed outside the pocket virtual circle C connecting the outer circumferential surface of the first sub back pressure pocket 1325a and the outer circumferential surface of the second sub back pressure pocket 1325b. On the other hand, the second end 1412b of the second guide groove 1412 may be formed between the first sub back pressure pocket 1325a and the second sub back pressure pocket 1325b in the circumferential direction.

The second guide groove 1412 may be formed on the same axis as the second discharge guide 142 to be described later and have a cross-sectional area larger than or equal to that of the second discharge guide 142 . Accordingly, the second guide groove 1412 may be in periodic communication with the second discharge guide 142 provided on the roller 134 when the roller 134 rotates.

Referring to FIGS. 4 to 6 , the second discharge guide part 142 according to the present embodiment may be formed through both side surfaces of the roller 134 in the axial direction. For example, the first end 142a of the second discharge guide 142 is opened to the lower surface of the roller 134 facing the sub-sliding surface 1321a, and the second end of the second discharge guide 142 (142b) may be opened to the upper surface of the roller 134 facing the surface of the main bearing (131).

The second discharge guide part 142 may penetrate in the axial direction. Accordingly, the second discharge guide 142 can be easily processed. However, the second discharge guide portion 142 does not necessarily have to be penetrated in the axial direction.

Although not shown in the drawing, the second discharge guide 142 is inclined with respect to the axial direction, for example, from the first end 142a to the second end 142b of the second discharge guide 142, the roller 134 ) may be formed inclined in the forward direction with respect to the direction of rotation. In this case, the refrigerant of the first discharge guide 141 may be discharged more quickly by receiving centrifugal force while passing through the second discharge guide 142 .

The second discharge guide part 142 may be formed at a position overlapping with the second guide groove 1412 of the first discharge guide part 141 described above in the axial direction. Accordingly, when the roller 134 rotates, the second discharge guide 142 may be in periodic communication with the second guide groove 1412 of the first discharge guide 141 .

One or more second discharge guides 142 may be formed. For example, the number of second discharge guides 142 may be greater than the number of first discharge guides 141, more precisely, the number of second guide grooves 1412. Accordingly, the second discharge guide part 142 communicates with the second guide groove 1412 per rotation of the roller 134 a plurality of times, exactly as many times as the number of the second discharge guide part 142, and the second guide groove The first discharge guide 141 including 1412 may communicate with the third discharge guide 143 once per rotation of the roller 134 .

The second discharge guide 142 is formed to correspond to the number of vanes 135 (or the number of compression chambers), and the first discharge guide 141 and the third discharge guide 143 are each formed one by one. It can be. In other words, the first discharge guide part 141 and the third discharge guide part 143 are formed on the same axis, and the second discharge guide part 142 is equally spaced along the circumferential direction, for example, the vane 135 In the case of three, each of the second discharge guides 142 may be formed at equal intervals along the circumferential direction at intervals of 120°. Accordingly, the second discharge guide 142 may communicate the first discharge guide 141 and the third discharge guide 143 every 120 ° based on the rotation angle of the roller (or rotation shaft) 134. .

Then, the discharge passage 140 is opened once every 120°, and the residual refrigerant not discharged from each of the compression chambers V1, V2, and V3 passes through each of the second discharge guides 142 to the inner space of the casing 110. (110a). Accordingly, during the compression stroke, the discharge passage 140 is blocked to prevent the refrigerant under compression from flowing out through the discharge passage 140, thereby preventing under-compression due to the discharge passage 140 in advance.

Although not shown in the drawing, the second discharge guide 142 is located between the adjacent vanes 1351 and 1352, 1352 and 1353, and 1353 and 1351, that is, in the compression chambers V1, V2, and V3, respectively. may be formed individually. Even in this case, residual refrigerant not discharged from each of the compression chambers V1 , V2 , and V3 may be discharged through each second discharge guide part 142 .

The second discharge guide part 142 may be formed in the same number or with the same cross-sectional area in each of the compression chambers V1 , V2 , and V3 . Accordingly, residual refrigerant not discharged from each compression chamber can be equally discharged.

The inner diameter of the second discharge guide part 142 may be formed to be equal to or wider than the width of the second guide groove 1412 . Accordingly, the refrigerant passing through the second guide groove 1412 of the first discharge guide part 141 moves to the second discharge guide part 142 without blockage, and the residual refrigerant can be quickly discharged.

Referring to FIGS. 4 to 6 , the third discharge guide part 143 according to the present embodiment may be formed to penetrate between both side surfaces of the main bearing 131 in the axial direction. For example, the first end 143a of the third discharge guide part 143 is opened to the main sliding surface 1311a of the main plate part 1311, and the second end 143b of the third discharge guide part 143 ) may be opened to the outer circumferential surface of the main boss portion 1312.

The third discharge guide 143 may be formed to communicate with the second guide groove 1412 of the first discharge guide 141 through the second discharge guide 142 . For example, when the second discharge guide part 142 penetrates in the axial direction, the first end 143a of the third discharge guide part 143 is the second end 1412b of the second guide groove 1412 and It may be formed to be positioned on the same axis.

Although not shown in the drawings, when the second discharge guide 142 is formed inclined, the first end of the second discharge guide 142 communicates with the second end 1412b of the second guide groove 1412. At this point, the first end 143a of the third discharge guide 143 may be formed to communicate with the second end 142b of the second discharge guide 142 . For example, the first end 143a of the third discharge guide 143 may be formed between the first main back pressure pocket 1315a and the second main back pressure pocket 1315b in the circumferential direction. Accordingly, the second discharge guide part 142 may be formed by penetrating the main boss part 1312 in the axial direction.

Although not shown in the drawings, the first end 143a of the third discharge guide 143 is a pocket virtual circle where the outer circumference of the first main back pressure pocket 1315a and the outer circumference of the second main back pressure pocket 1315b are connected ( C) may be formed outside. In this case, the second discharge guide part 142 is formed by penetrating the main boss part 1312 obliquely with respect to the axial direction, or a guide protrusion (not shown) extending in the radial direction on the outer circumferential surface of the main boss part 1312. It can be formed by penetrating in the axial direction.

The number of third discharge guides 143 may be smaller than the number of second discharge guides 142 . For example, the third discharge guide 143 is formed only one by one with the first discharge guide 141, and may be formed to be positioned on the same axis. In this case, the second discharge guide 142 is formed at equal intervals along the circumferential direction of the number of compression chambers V1, V2, and V3, that is, three, and each second discharge guide 142 is on the same axis. can be formed in Accordingly, the third discharge guide 143 may communicate with the first discharge guide 141 once per rotation of the roller 134 .

Although not shown in the drawings, the third discharge guide 143 may be formed in a different number from the first discharge guide 141 . For example, only one third discharge guide 143 is formed, but a plurality of first discharge guides 141 may be formed, and conversely, a plurality of third discharge guides 143 are formed, and the first One discharge guide 141 may be formed. However, even in these cases, each second discharge guide 142 is formed on the same axis, and the third discharge guide 143 is formed with the first discharge guide 141 once per rotation of the roller 134. It can be formed to communicate.

The inner diameter of the third discharge guide part 143 may be greater than or equal to the inner diameter of the second discharge guide part 142 . For example, the cross-sectional area of the first end 143a of the third discharge guide 143 may be greater than or equal to the cross-sectional area of the second end 142b of the second discharge guide 142 . Accordingly, the refrigerant passing through the second discharge guide part 142 moves to the third discharge guide part 143 without clogging, so that residual refrigerant can be quickly discharged.

The second end 143b of the third discharge guide 143 may open toward the inner space 110a of the casing 110 from the outer circumferential surface of the main boss 1312 . For example, based on the upper surface of the main plate part 1311, the height H3 of the second end 143b of the third discharge guide part 143 is the height of the discharge space part 1372 of the discharge muffler 137 ( H1) can be formed higher. In other words, the second end 143b of the third discharge guide 143 may be opened to the outer circumferential surface of the main boss 1312 at a position higher than the discharge space 1372 of the discharge muffler 137 . Accordingly, the refrigerant passing through the third discharge guide 143 may be directly discharged into the inner space 110a of the casing 110 without passing through the discharge space 1372a of the discharge muffler 137 . Through this, the refrigerant suppresses the increase in the internal pressure of the discharge muffler 137 so that the discharge valves 1361, 1362, and 1363 are quickly opened, and at the same time suppresses the vortex phenomenon in the discharge space 1372a, so that each discharge port ( In 1313a, 1313b, and 1313c), the refrigerant can be discharged more rapidly.

In addition, the second end 143b of the third discharge guide 143 passes through the third discharge guide 143 as it is opened to the outer circumferential surface of the main boss 1312, and the inner space 110a of the casing 110 The refrigerant discharged to ) is a gap between the inner circumferential surface of the stator 121 and the inner circumferential surface of the rotor 122, or an inner void of the stator 121, or a gap between the outer circumferential surface of the stator 121 and the inner circumferential surface of the casing 110. It is smoothly guided toward the discharge pipe 116 and can move quickly toward the discharge pipe 116 .

Although not shown in the drawing, the second end 143b of the third discharge guide 143 may be opened to the top surface of the main boss 1312. In this case, since the third discharge guide portion 143 is formed through a single process, the third discharge guide portion 143 can be easily processed.

The rotary compressor according to the present embodiment as described above has the following operational effects.

Referring back to FIG. 3, as the vanes 1351, 1352, and 1353 rotate together with the roller 134, the corresponding compression chambers V1, V2, and V3 move from the first outlet 1313a to the third outlet 1313c. ) to pass through the respective discharge ports 1313a, 13131b, and 1313c in turn. At this time, most of the refrigerant compressed in the corresponding compression chambers (V1, V2, V3) is discharged to the discharge space (1372a) of the discharge muffler (137) through the respective discharge ports (1313a) (13131b) (1313c), and the casing (110) is discharged into the inner space (110a) of. However, some of the refrigerant is not discharged past the third outlet 1313c and remains as residual refrigerant in the residual space S between the third outlet 1313c and the contact point P.

Therefore, in this embodiment, the discharge passage 140 is provided at the rear side of the third discharge port 1313 to discharge the refrigerant remaining in the residual space S to the inner space 110a of the casing 110. In other words, as in the present embodiment, the first discharge guide part 141 forming a part of the discharge passage 140 is connected to the third discharge port 1313c2 or the remaining space S of the rear side of the third discharge port 1313c, which is the final discharge port. When formed in an overlapping position, the refrigerant remaining in the residual space (S) is a discharge passage 140 composed of a first discharge guide part 141, a second discharge guide part 142 and a third discharge guide part 143 It can be directly discharged to the inner space (110a) of the casing (110) through. Accordingly, it is possible to minimize the remaining high-pressure refrigerant in the residual space (S) to lower the motor input or suppress the behavior of the vane from becoming unstable.

8A to 8C are schematic diagrams showing a process in which residual refrigerant is discharged through the discharge passage according to the present embodiment. For convenience, the inner diameters of the second guide groove, the second discharge guide, and the third discharge guide are shown differently in FIGS. 8A to 8C. However, the inner diameters of the second guide groove, the second discharge guide portion, and the third discharge guide portion may be formed differently as shown in the drawings or may be identical to each other.

8A shows a state in which the roller 134 rotates and the corresponding vane 135 reaches a position adjacent to the third discharge port 1313c. In this state, the corresponding vane 135 is still in the process of passing through the third discharge port 1313c, so the third discharge port 1313c is still open, and accordingly, the remaining space S communicated with the third discharge port 1313c is also It remains open, not sealed. At this time, the second discharge guide part 142 provided on the roller 134 still reaches between the first discharge guide part 141 of the sub bearing 132 and the third discharge guide part 143 of the main bearing 131. It becomes an uncommunicative state. Then, the refrigerant in the remaining space (S), together with the refrigerant in the compression chamber, passes through the third outlet (1313c) until the corresponding vane (135) passes through the rear side third outlet (1313c2) forming the third outlet (1313c). It is discharged into the inner space (110a) of the casing (110) through.

8B shows a state in which the roller 134 further rotates and the corresponding vane 135 just passes through the third discharge port 1313c. In this state, the corresponding vane 135 is located between the third discharge port 1313c and the remaining space S, and the remaining space S is separated from the third discharge port 1313c and becomes sealed. At this time, the second discharge guide part 142 provided on the roller 134 reaches between the first discharge guide part 141 of the sub bearing 132 and the third discharge guide part 143 of the main bearing 131, It becomes a state of communication. Then, the refrigerant in the residual space (S) passes through the first discharge guide part 141, the second discharge guide part 142, and the third discharge guide part 143 in order to enter the inner space 110a of the casing 110. can be emitted as Accordingly, even if some of the refrigerant remains because the residual space (S) is sealed, the residual refrigerant is discharged to the inner space (110a) of the casing 110 through the discharge passage 140, so that the high-pressure refrigerant is discharged to the residual space (S). What remains can be suppressed.

8C shows a state in which the roller 134 further rotates and the corresponding vane 135 passes through the third outlet 1313c and almost reaches the contact point P. In this state, the preceding vane has already passed through the third discharge port 1313c, but the following vane has yet to reach the third discharge port 1313c, so the third discharge port 1313c is open. Accordingly, the remaining space S communicated with the third discharge port 1313c is not sealed and remains open. At this time, the second discharge guide part 142 provided on the roller 134 passes between the first discharge guide part 141 of the sub bearing 132 and the third discharge guide part 143 of the main bearing 131, become incompetent. Then, the refrigerant in the residual space (S), together with the refrigerant in the subsequent compression chamber, passes through the casing ( 110) is discharged into the inner space (110a).

In this way, as the residual refrigerant remaining in the compression space even after the discharge stroke is discharged to the inner space of the casing through the discharge passage, it is possible to minimize the refrigerant remaining in the compression space even after the discharge stroke. At the same time, as the discharge passage is periodically opened, leakage of the refrigerant during the compression stroke can be suppressed, thereby preventing under-compression from occurring.

In addition, as a discharge guide is further provided in addition to the discharge port to form a discharge passage, the discharge effective area for discharging the compressed refrigerant into the inner space of the casing can be expanded, and through this, the refrigerant compressed in the compression chamber during the discharge stroke can be more rapidly discharged. It can be discharged in such a way that overcompression loss can be suppressed.

In addition, the pressure acting on the front surface of the vane can be equalized by suppressing the high-pressure refrigerant from remaining in the residual space, and through this, the pressure difference acting on the front and rear surfaces of the vane can be eliminated, resulting in vane jumping. can suppress In addition, through this, it is possible to suppress abrasion of the front surface of the vane or the inner circumferential surface of the cylinder facing the vane, and at the same time, vibration noise due to vibration of the vane can be reduced. In addition, suction loss can be reduced by suppressing the high-pressure refrigerant from flowing into the suction side beyond the contact point P.

In addition, the discharge passage including the discharge passage may extend to the circumferential range of the compression chamber or outside the circumferential range of the compression chamber, and through this, continuous discharge is possible during the discharge stroke, thereby reducing pressure pulsation.

In addition, the rotary compressor according to the present embodiment, when using a high-pressure refrigerant such as R32, R410a, or CO ₂ , can obtain the above-described effect more significantly.

On the other hand, the case where there is another embodiment for the discharge passage is as follows.

That is, in the above-described embodiment, the inlet of the discharge passage is formed between the discharge port and the residual space, but in some cases, the inlet of the discharge passage may be formed on the front side of the discharge port.

9 is a plan view showing another embodiment of the discharge passage.

Referring to FIG. 9 , in this embodiment, the discharge passage 140 may include a first discharge guide 141 , a second discharge guide 142 and a third discharge guide 143 . Since the basic configuration of the first discharge guide unit 141, the second discharge guide unit 142, and the third discharge guide unit 143 and the operational effects thereof are the same as those of the foregoing embodiment, a detailed description thereof is as described above. It is replaced with a description of an embodiment.

However, the first discharge guide part 141 according to this embodiment is composed of a first guide groove 1411 and a second guide groove 1412, and the first guide groove 1411 is the final discharge port, the rear side third. It may be located on the front side of the discharge port 1313c2. For example, the first guide groove 1411 may be formed to be located on the front side in the circumferential direction rather than the front side third discharge port 1313c1. Accordingly, a part of the refrigerant that has passed through the second discharge port 1313b flows into the first discharge guide part 141 forming the inlet of the discharge passage 140 before moving to the third discharge port 1313c1 on the front side, and the refrigerant may be previously discharged into the inner space 110a of the casing 110 through the second discharge guide 142 and the third discharge guide 143.

Even in this case, the first guide groove 1411 may overlap with the third discharge port 1313c1 on the front side by approximately 50% or more in the axial direction. Accordingly, it is possible to suppress under-compression of the refrigerant in the compression chamber due to the discharge passage 140 .

As described above, when the first guide groove 1411 of the first discharge guide part 141 constituting the inlet of the discharge passage 140 is located at the front of the third discharge port 1313c1 on the front side, the third discharge port 1313c The effective discharge area of can be expanded. Accordingly, the refrigerant compressed in the compression chamber can be quickly discharged not only through the third discharge port 1313c but also through the discharge passage 140, thereby reducing the amount of undischarged refrigerant from the corresponding compression chamber. Through this, the residual amount of refrigerant that is not discharged from the compression chamber and moves to the residual space is reduced, so that the above-described reduction in motor efficiency due to overcompression in the compression space and wear and vibration noise due to vibration of the vane can be suppressed.

Although not shown in the drawing, when the third discharge port 1313c2 on the rear side is formed at a position widened at least 5°, which is the minimum sealing distance α from the contact point P, the first guide groove 1411 is formed on the rear side third discharge port 1313c2. The front side of the discharge port 1313c2, for example, may be formed in a section on the rear side of the rear side third discharge port 1313c2 on the front side of the front side third discharge port 1313c1. Even in these cases, the first guide groove 1411 is formed to overlap at least 50% in the axial direction with the front third discharge port 1313c1 or/and the rear side third discharge port 1313c2 at a position securing the minimum sealing distance. It may be desirable to be In addition, even in these cases, the operation and effect are similar to those of the above-described embodiment, so a description thereof will be omitted.

On the other hand, the case where there is another embodiment for the discharge passage is as follows.

That is, in the above-described embodiments, the inlet of the discharge passage is formed eccentrically on the rear side or front side with respect to the discharge port, but in some cases, the inlet of the discharge passage may be formed substantially on the same axis as the discharge port.

10 is a plan view showing another embodiment of the discharge passage.

Referring to FIG. 10 , in this embodiment, the discharge passage 140 may include a first discharge guide 141 , a second discharge guide 142 and a third discharge guide 143 . Since the basic configuration of the first discharge guide unit 141, the second discharge guide unit 142, and the third discharge guide unit 143 and the operational effects thereof are the same as those of the foregoing embodiment, a detailed description thereof is as described above. It is replaced with a description of an embodiment.

However, the first discharge guide part 141 according to this embodiment is composed of a first guide groove 1411 and a second guide groove 1412, and the first guide groove 1411 is the third discharge port that is the final discharge port ( 1313c) and at least a part may be located on the same axis. For example, the rear side third discharge port 1313c2 is formed at a position 5° corresponding to the minimum sealing distance α from the contact point P, and the first guide groove 1411 is the rear side third discharge port 1313c2 ) and may be located approximately on the same axis.

In this case, the first guide groove 1411 may be located between the rear third discharge port 1313c2 and the front third discharge port 1313c1. For example, the first guide groove 1411 is positioned rearward (or on the same axis) as the front third discharge port 1313c1, but positioned forward (or on the same axis) as the rear side third discharge port 1313c2. It can be. Accordingly, the first guide groove 1411 may partially communicate with the rear third discharge port 1313c2 and the front third discharge port 1313c1.

As described above, when the first guide groove 1411 of the first discharge guide part 141 constituting the entrance of the discharge passage 140 is located at the front of the rear-side third discharge port 1313c2, which is the final discharge port, the discharge passage ( 140) serves as a kind of discharge port or bypass passage. That is, a part of the refrigerant passing through the second discharge port 1313b flows into the first discharge guide part 141 forming the entrance of the discharge passage 140, and the refrigerant flows into the second discharge guide forming the discharge passage 140. It can also be discharged into the inner space 110a of the casing 110 through the portion 142 and the third discharge guide 143 .

Accordingly, the effective discharge area of the third discharge port 1313c is enlarged while the discharge passage 140 serves as the third discharge port 1313c, so that the refrigerant compressed in the compression chamber can be discharged more quickly. Through this, the residual amount of refrigerant that is not discharged from the compression chamber and moves to the residual space is reduced, so that the above-described reduction in motor efficiency due to overcompression in the compression space and wear and vibration noise due to vibration of the vane can be suppressed.

In addition, as the first guide groove 1411 is located on the front side of the rear-side third discharge port 1313c2, but is located equal to or behind the front-side third discharge port 1313c1, the refrigerant in the compression chamber is in an under-compressed state. leakage can be prevented.

Although not shown in the drawings, when the third discharge port 1313c2 on the rear side is formed at a position of 5°, which is the minimum sealing distance α from the contact point P, the first guide groove 1411 is the third discharge port on the front side. It may be formed so as to be located on the front side of (1313c1). In other words, the first guide groove 1411 may be formed in a section from a position overlapping the rear third discharge port 1313c2 to the front side of the front third discharge port 1313c1. Even in these cases, the first guide groove 1411 is formed to overlap at least 50% in the axial direction with the front third discharge port 1313c1 or/and the rear side third discharge port 1313c2 at a position securing the minimum sealing distance. It may be desirable to be In addition, even in these cases, the operation and effect are similar to those of the above-described embodiment, so a description thereof will be omitted.

On the other hand, the case where there is another embodiment for the discharge passage is as follows.

That is, in the above-described embodiment, only one inlet of the discharge passage is formed, but in some cases, a plurality of inlets of the discharge passage may be formed.

11 is a plan view showing another embodiment of the discharge passage.

Referring to FIG. 11 , in this embodiment, the discharge passage 140 may include a first discharge guide 141 , a second discharge guide 142 and a third discharge guide 143 . Since the basic configuration of the first discharge guide unit 141, the second discharge guide unit 142, and the third discharge guide unit 143 and the operational effects thereof are the same as those of the foregoing embodiment, a detailed description thereof is as described above. It is replaced with a description of an embodiment.

However, the first discharge guide part 141 according to this embodiment is composed of a first guide groove 1411 and a second guide groove 1412, and the first guide grooves 1411a and 1411b are two pairs. can be formed as

In this case, the second guide groove 1412 communicates with either one of the first guide grooves (eg, the first guide groove on the rear side) 1411b among the two first guide grooves 1411a and 1411b, and 1 guide groove 1411 may communicate with each other. For example, as shown in FIG. 11, the plurality of first guide grooves 1411a and 1411b are spaced apart by a predetermined distance along the circumferential direction, but are connected to each other through an intermediate connection groove 1411c, or, although not shown in the drawing, both first guide grooves 1411a and 1411b. Some of the guide grooves 1411a and 1411b may be formed to overlap each other in the circumferential direction.

In this case, the discharge passage arc angle β is greater than or equal to the vane seam angle θ as described above, that is, the vane seam angle θ is 120 °, but the discharge passage arc angle β is approximately 120 °. It can be formed greater than or equal to. Accordingly, the discharge passage including the discharge port and the discharge passage 140 extends to the circumferential range of the compression chamber or outside the circumferential range of the compression chamber, thereby minimizing the residual amount of refrigerant in the compression chamber or residual space (S). there is. In addition, as the arc length of the discharge passage is formed equal to or longer than the arc length of the compression chamber, continuous discharge is possible and pressure pulsation can be reduced.

As described above, when a plurality of first guide grooves 1411a and 1411b are formed, the gap between the first sub back pressure pocket 1325a and the second sub back pressure pocket 1326b is narrow, so that the second guide groove is formed between the pockets. Even when only one groove 1412 is formed, a plurality of first guide grooves 1411a and 1411b can be formed to discharge residual refrigerant or compressed refrigerant more quickly. Through this, overcompression in the final compression chamber can be suppressed to further increase motor efficiency.

On the other hand, the case where there is another embodiment for the discharge passage is as follows.

That is, the aforementioned discharge passage is formed with the same inner diameter, but in some cases, the inner diameter of the discharge passage may be formed differently.

12 is a perspective view showing another embodiment of the discharge passage, and FIG. 13 is a cross-sectional view of FIG.

12 and 13, the discharge passage 140 according to the present embodiment may include a first discharge guide 141, a second discharge guide 142 and a third discharge guide 143. there is. Since the basic configuration of the first discharge guide unit 141, the second discharge guide unit 142, and the third discharge guide unit 143 and their operational effects are similar to those of the foregoing embodiments, a detailed description thereof will be given in the foregoing. instead of a description of one embodiment.

However, expansion grooves 1421 and 1422 having an enlarged cross-sectional area may be formed at one or both ends of the second discharge guide 142 according to the present embodiment. For example, the expansion grooves 1421 and 1422 are formed at both ends of the second discharge guide 142, respectively, and each of the expansion grooves 1421 and 1422 may be formed in the same shape or different shapes. It could be. Hereinafter, an example in which the expansion grooves 1421 and 1422 are formed in the same shape at both ends of the first discharge guide part 142 will be described.

For example, the inner diameter of the second discharge guide part 142 is formed to be the same as the width (or inner diameter) of the second guide groove 1412 of the first discharge guide part 141, and each expansion groove 1421 1422 may be formed larger than inner diameters of the first end 142a and the second end 142b of the second discharge guide 142 .

The expansion groove 1421 may be formed concentrically with the first end 142a of the second discharge guide 142, and in some cases may be formed on the first end 142a of the second discharge guide 142. It can be formed eccentrically.

As described above, when the expansion grooves 1421 and 1422 are formed at both ends of the second discharge guide 142, the communication cycle between the first discharge guide and the second discharge guide 142 and the second discharge guide The communication period between the 142 and the third discharge guide 143 may increase. Accordingly, the residual refrigerant may be discharged more quickly.

Although not shown in the drawing, the expansion groove may be formed in the second guide groove 1412 of the first discharge guide 141 facing the first end 142a of the second discharge guide 142, The second end 142b of the second discharge guide part 142 may be formed on the first end 143a of the third discharge guide part 143 facing each other. Alternatively, the expansion groove may be formed in the first end 142a of the second discharge guide 142 and the second guide groove 1412 of the first discharge guide 141 facing the same, respectively, and the second discharge guide The first end 143a of the third discharge guide 143 facing the second end 142b of the guide 142 may be formed, respectively. Actions and effects of these embodiments may be similar to those of the above-described embodiments, or the discharge effect of residual refrigerant may be improved.

On the other hand, the case where there is another embodiment for the discharge passage is as follows.

That is, the second discharge guide portion constituting a part of the aforementioned discharge passage passes through the roller in the axial direction, but may be inclined with respect to the axial direction in some cases.

14 is an exploded perspective view showing another embodiment of the discharge passage, FIG. 15 is an assembled sectional view of FIG. 14, and FIG. 16 is a schematic view showing the discharge passage of FIG. 14 in an open state.

14 to 16, in this embodiment, the discharge passage 140 may include a first discharge guide 141, a second discharge guide 142 and a third discharge guide 143. . Since the basic configuration of the first discharge guide unit 141, the second discharge guide unit 142, and the third discharge guide unit 143 and their operational effects are similar to those of the foregoing embodiments, a detailed description thereof will be given in the foregoing. instead of a description of one embodiment.

However, the first end 142a of the first discharge guide part 141 and the second discharge guide part 142 according to this embodiment is outside the first sub pocket 1325a and the second sub back pressure pocket 1325b. . Between, in other words, it may be formed to be located inside the pocket imaginary circle (C). Accordingly, the first discharge guide 141 may be formed as a single guide groove, unlike the above-described embodiments.

For example, the first discharge guide portion 141 may be formed of only the first guide groove 1411 excluding the second guide groove 1412 in the above-described embodiment. In this case, the first guide groove 1411 may be formed larger than the inner diameter of the third discharge port 1313 so that a portion of the first guide groove 1411 is located inside the outer circumferential surface 1342 of the roller 134 or may be formed in a long groove shape in the radial direction. there is.

As described above, when the first discharge guide portion 141 is formed of only one guide groove, that is, the first guide groove 1411, not only the processing of the first discharge guide portion 141 is easy, but also the first discharge guide portion 141. As the discharge guide 141 is located outside the first sub back pressure pocket 1325a and the second sub back pressure pocket 1325b, the degree of freedom in designing the shape or location of the first discharge guide 141 can be increased. .

Although not shown in the drawing, when the first discharge guide part 141 is formed of the first guide groove 1411 and the second guide groove 1412 as in the above-described embodiment, the length of the second guide groove 1412 can be formed short. In this case, as the overall length of the first discharge guide 141 is shortened, processing of the first discharge guide 141 becomes easy, and the first discharge guide 141 has a first sub back pressure pocket 1325a. ) and the second sub back pressure pocket 1325b, it is possible to increase the degree of freedom in designing the shape or location of the first discharge guide part 141.

In addition, as the first discharge guide part 141 and the third discharge guide part 143 are positioned on different axes, the second discharge guide part 142 may be inclined. For example, the first end 142a of the second discharge guide 142 is formed outside the pocket virtual circle C so as to be located on the same axis as the first discharge guide 141, and the second discharge guide The second end 142b of the portion 142 may be formed within the pocket imaginary circle C so as to be positioned on the same axis as the third discharge guide portion 143 .

As the second discharge guide part 142 is formed inclined as described above, the refrigerant passing through the second discharge guide part 142 is subjected to centrifugal force, and as a result, the residual space (S) or the compression space (V) during the discharge stroke The refrigerant in the second discharge guide portion 142 can be more rapidly moved to the third discharge guide portion 143 and discharged.

On the other hand, the case where there is another embodiment for the discharge passage is as follows.

That is, in the above-described embodiments, the outlet of the discharge passage is formed through the main boss of the main bearing, but in some cases, the inlet of the discharge passage may be formed substantially on the same axis as the discharge port.

17 and 18 are perspective and cross-sectional views showing another embodiment of the discharge passage.

17 and 18, the discharge passage 140 in this embodiment may include a first discharge guide 141, a second discharge guide 142 and a third discharge guide 143 . Since the basic configuration of the first discharge guide unit 141, the second discharge guide unit 142, and the third discharge guide unit 143 and the operational effects thereof are the same as those of the foregoing embodiment, a detailed description thereof is as described above. It is replaced with a description of an embodiment.

However, the first end 143a of the third discharge guide part 143 according to this embodiment is the lower surface of the main plate part 1311 forming the main sliding surface 1311a facing the roller 134 in the axial direction. The second end 143b of the third discharge guide 143 may be opened from the upper surface of the main plate 1311 toward the discharge space 1372 of the discharge muffler 137. In other words, as the second end 143b of the third discharge guide 143 is formed on the main plate 1311, the height H3' of the second end 143b of the third discharge guide 143 is It may be formed lower than the height H1 of the discharge space 1372 .

In this case, the second stage 143b of the third discharge guide 143 is located between the first main back pressure pocket 1315a and the second main back pressure pocket 1315b, and each of the discharge valves 1361, 1362, and 1363 ) and may be formed to be spaced apart. Accordingly, the refrigerant discharged to the discharge space 1372a of the discharge muffler 137 through the third discharge guide 143 is discharged from the discharge muffler 137 without being blocked by the discharge valves 1361, 1362, and 1363. It can always be open to space 1372a.

As described above, when the third discharge guide portion 143 is formed through the main plate portion 1311, the length of the third discharge guide portion 143 is shortened to facilitate the third discharge guide portion 143. can be processed In particular, even when the inner diameter of the third discharge guide part 143 is small, it can be easily processed, thereby reducing the manufacturing cost.

In addition, as the third discharge guide part 143 is formed on the main plate part 1311, the length of the first discharge guide part 141, in other words, the length of the second guide groove 1412 can be shortened. The discharge guide part 141 can be easily processed. In addition, in some cases, the second guide groove 1412 is outside the first main back pressure pocket and the second main back pressure pocket, that is, between the outer circumferential surface of the first main back pressure pocket 1315a and the second main back pressure pocket 1315b. It may be formed outside the pocket imaginary circle (C) connecting the outer circumferential surface. In this case, the width of the second guide groove 1412 may be formed wide or the second guide groove 1412 may be formed in plural numbers, so that the refrigerant may be discharged more rapidly.

Meanwhile, although not shown in the drawings, discharge ports 1313a, 1313b, and 1313c may be formed in the sub-bearing 132. In this case, the first discharge guide part 141 constituting the discharge passage 140 is attached to the main bearing 131, the second discharge guide part 142 is attached to the roller 134, and the third discharge guide part 143 is attached to the roller 134. Each may be formed on the sub-bearing 132. Even in this case, the configuration of the first discharge guide unit 141, the second discharge guide unit 142, and the third discharge guide unit 143 and their operational effects may be identical to those of the above-described embodiments. A description thereof is replaced with a description of the above-described embodiments.

In addition, in the above-described embodiments, the discharge grooves 1314a and 1314b may be extended and formed in some discharge ports. For example, discharge grooves 1314a and 1314b are extended in the first discharge port 1313a and the second discharge port 1313b, respectively, and each discharge groove 1314a and 1314b is in the compression direction (roller rotation direction). It can be extended in an arc shape along. Accordingly, the refrigerant not discharged from the preceding compression chamber is guided to the discharge ports 1313a and 1313b communicating with the following compression chamber through the respective discharge grooves 1314a and 1314b, and is discharged together with the refrigerant compressed in the subsequent compression chamber. can be made Through this, it is possible to increase compressor efficiency by suppressing overcompression by minimizing residual refrigerant in the compression space (V).

110: casing 110a: inner space
110b: low oil space 110c: oil separation space
111: middle shell 112: lower shell
113: upper shell 115: suction pipe
116: discharge pipe 120: drive motor
121: stator 122: rotor
123: rotary shaft 125: oil passage
126a: first oil through hole 126b: second oil through hole
127: oil pickup 130: compression unit
131: main bearing 1311: main plate part
1311a: main sliding surface 1312: main bush
1312a: main bearing hole 1312b: main bearing surface
1312c: first oil groove 1313, 1313a, 1313b, 1313c: discharge port
1313c1: Front side third discharge port 1313c2: Rear side third discharge port
1314: discharge groove 1315a: first main back pressure pocket
1315b: second main back pressure pocket 1316a: first main bearing protrusion
1316b: second main bearing protrusion 132: sub-bearing
1321: sub plate portion 1321a: sub sliding surface
1322: sub bush part 1322a: sub bearing hole
1322b: sub-bearing surface 1322c: oil groove
1325a: first sub back pressure pocket 1325 b: second sub back pressure pocket
1326a: first sub-bearing protrusion 1326b: second sub-bearing protrusion
133: cylinder 1331: inlet
1332: inner peripheral surface of cylinder 1332a: proximal portion
1332b: circular portion 1332c: curved portion
134: roller 1341: soccer hole
1342: outer circumferential surface of the roller 1343a, 1343b, 1343c: vane slot
1344a, 1344b, 1344c: back pressure chamber 135, 1351, 1352, 1353: vane
1351a, 1352a, 1353a: front end surface of vane 1351b, 1352b, 1353b: rear end surface of vane
1361, 1362, 1363: discharge valve 137: discharge muffler
1371: muffler fixing part 1372: discharge space part
1372a: discharge space 1372b: bearing through hole
140: residual refrigerant discharge passage 141: first discharge guide
1411: first guide groove 1411a: front side first guide groove
1411b: rear side first guide groove 1411c: intermediate connection groove
1412: second guide groove 1412a: first end of the second guide groove
1412b: second end of the second guide groove 142: second discharge guide
142a: first end of the second discharge guide 142b: second end of the second discharge guide
143: third discharge guide 143a: first stage of third discharge guide
143b: 2nd stage of the 3rd discharge guide C: Pocket Virtual Chamber
D: discharge interval H1: height of discharge space
H2: Height of the main bush H3, H3': Height of the outlet of the discharge passage
O: 1st origin O': 2nd origin
Or: the center of the roller Oc: the center of the outer diameter of the cylinder
P: proximity point (contact point) Q1,Q2,Q3,Q4:
S: residual space V: compression space
V1, V2, V3: 1st, 2nd, 3rd compression chamber α: Minimum sealing distance
β: Discharge passage arc angle θ: Vane angle

Claims (28)

casing;
a cylinder provided in the inner space of the casing to form a compression space;
a roller provided on a rotating shaft to be rotatable in the inner space of the cylinder and positioned eccentrically with respect to the center of the compression space so as to have a contact point close to the inner circumferential surface of the cylinder;
a vane that is slidably inserted into a vane slot provided in the roller and rotates together with the roller;
Main bearings and sub-bearings disposed on both sides of the cylinder in the axial direction, respectively, to form a compression space together with the cylinder; and
And a discharge passage for discharging the refrigerant from the compression space to the inner space of the casing,
The discharge passage,
a first discharge guide provided in the main bearing or the sub-bearing;
a second discharge guide unit passing between both ends of the roller in the axial direction and communicating with the first discharge guide unit; and
A third discharge guide provided at a bearing opposite to the bearing having the first discharge guide with the roller as the center and communicating with the first discharge guide through the second discharge guide,
The first discharge guide unit,
A rotary compressor formed in a bearing not provided with a discharge port among the main bearing and the sub-bearing. According to claim 1,
The discharge passage,
A rotary compressor that is periodically opened according to the rotation of the roller. According to claim 1,
The discharge passage,
A rotary compressor provided with a plurality at equal intervals along the circumferential direction of the roller. According to claim 1,
A plurality of vane slots are formed along the circumferential direction of the roller,
Part of the discharge passage,
A rotary compressor formed between the plurality of vane slots, respectively. casing;
a cylinder provided in the inner space of the casing to form a compression space;
a roller provided on a rotating shaft to be rotatable in the inner space of the cylinder and positioned eccentrically with respect to the center of the compression space so as to have a contact point close to the inner circumferential surface of the cylinder;
a vane that is slidably inserted into a vane slot provided in the roller and rotates together with the roller;
Main bearings and sub-bearings disposed on both sides of the cylinder in the axial direction, respectively, to form a compression space together with the cylinder; and
And a discharge passage for discharging the refrigerant from the compression space to the inner space of the casing,
The discharge passage,
a first discharge guide provided in the main bearing or the sub-bearing;
a second discharge guide unit passing between both ends of the roller in the axial direction and communicating with the first discharge guide unit; and
A third discharge guide provided at a bearing opposite to the bearing having the first discharge guide with the roller as the center and communicating with the first discharge guide through the second discharge guide,
The first discharge guide unit,
a first guide groove communicating with the compression space; and
One end is in communication with the first guide groove, and the other end includes a second guide groove in communication with the second discharge guide part,
The second guide groove extends closer to the center of rotation of the roller than the first guide groove. According to claim 5,
The second discharge guide unit,
The rotary compressor is in periodic communication with at least one discharge guide part among the first discharge guide part and the third discharge guide part according to the rotation of the roller. According to claim 5,
The first discharge guide part and the third discharge guide part,
Rotary compressors communicating with each other through the second discharge guide according to the rotation angle of the roller. According to claim 5,
The number of the second discharge guides,
A rotary compressor formed to exceed the number of the first discharge guides or the number of the third discharge guides. According to claim 5,
Each of the first discharge guide and the third discharge guide is provided,
The second discharge guide unit,
A plurality of rotary compressors provided and formed at predetermined intervals along the circumferential direction. According to claim 9,
The first discharge guide and the third discharge guide facing the second discharge guide are formed on the same axis,
The second discharge guide portion penetrates in the axial direction of the rotary compressor. According to claim 9,
The first discharge guide and the third discharge guide facing the second discharge guide are formed on different axes,
The second discharge guide portion is obliquely penetrated with respect to the axial direction of the rotary compressor. delete According to claim 5,
At least one discharge port is formed in the main bearing or the sub-bearing,
The first guide groove,
A rotary compressor at least partially overlapping the discharge port in an axial direction. According to claim 13,
The rotary compressor of claim 1 , wherein the first guide groove overlaps the discharge port by at least 50% in an axial direction. According to claim 5,
At least one discharge port is formed in the main bearing or the sub-bearing,
The first guide groove,
The rotary compressor of claim 1 , wherein the first guide groove is formed to have a cross-sectional area larger than or equal to a cross-sectional area of the discharge port overlapping in the axial direction. According to claim 5,
At least one discharge port is formed in the main bearing or the sub-bearing,
The first guide groove,
The rotary compressor wherein the first guide groove is positioned at a rear side relative to the rotational direction of the roller relative to the discharge port overlapping in the axial direction. According to claim 16,
The first guide groove,
A rotary compressor comprising a plurality of grooves along a circumferential direction, and intermediate connection grooves for communicating the plurality of first guide grooves with each other between the plurality of first guide grooves. According to claim 5,
At least one discharge port is formed in the main bearing or the sub-bearing,
The first guide groove,
The rotary compressor is formed so that the first guide groove is positioned at a front side relative to the rotational direction of the roller relative to the discharge port overlapping in the axial direction. According to claim 18,
A plurality of discharge ports are formed in the main bearing or the sub-bearing,
The first guide groove,
A rotary compressor positioned between the plurality of discharge ports to communicate with each of the plurality of discharge ports. According to claim 5,
A plurality of back pressure pockets having different pressures are formed spaced apart from each other in a circumferential direction on one side surface of the main bearing and one side surface of the sub bearing facing the roller in the axial direction,
The second guide groove,
A rotary compressor formed thinner and longer than the first guide groove and provided between the plurality of back pressure pockets in a circumferential direction. According to claim 5,
The vane slot is formed in plurality along the circumferential direction,
The second discharge guide unit,
A rotary compressor provided between each of the vane slots adjacent to each other in the circumferential direction. According to claim 21,
An expansion groove having an enlarged cross-sectional area is formed at both ends of the second discharge guide and at least one end of the end of the first discharge guide and the end of the third discharge guide facing the second discharge guide. According to claim 5,
A plurality of back pressure pockets having different pressures are formed spaced apart from each other in a circumferential direction on one side surface of the main bearing and one side surface of the sub bearing facing the roller in the axial direction,
The third discharge guide unit,
A rotary compressor provided between the plurality of back pressure pockets in a circumferential direction. According to claim 5,
The main bearing or the sub-bearing is provided with a discharge muffler accommodating the discharge port,
The third discharge guide unit,
A rotary compressor that opens toward the inner space of the casing from the outside of the discharge muffler. According to claim 24,
The main bearing or the sub-bearing,
a plate portion coupled to an axial side of the cylinder; and
A boss portion extending in an axial direction from one side of the plate portion in an axial direction and passing through the rotational shaft;
The third discharge guide unit,
A rotary compressor opening toward the inside of the casing from the boss portion. According to claim 5,
The main bearing or the sub-bearing is provided with a discharge muffler accommodating the discharge port,
The third discharge guide unit,
A rotary compressor that opens toward the inner space of the discharge muffler. The method of claim 26,
The main bearing or the sub-bearing,
a plate portion coupled to an axial side of the cylinder; and
A boss portion extending in an axial direction from the plate portion and passing through the rotation shaft;
The third discharge guide unit,
A rotary compressor penetrating the plate portion. The method of any one of claims 5 to 11 and 13 to 27,
One of the main bearing and the sub-bearing is provided with a discharge port that is opened and closed by a discharge valve,
The first discharge guide unit,
A rotary compressor formed in a bearing not provided with the discharge port.

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